WO2015050143A1 - Double-row tapered roller bearing unit and method for manufacturing same - Google Patents

Double-row tapered roller bearing unit and method for manufacturing same Download PDF

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Publication number
WO2015050143A1
WO2015050143A1 PCT/JP2014/076215 JP2014076215W WO2015050143A1 WO 2015050143 A1 WO2015050143 A1 WO 2015050143A1 JP 2014076215 W JP2014076215 W JP 2014076215W WO 2015050143 A1 WO2015050143 A1 WO 2015050143A1
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WO
WIPO (PCT)
Prior art keywords
inner ring
shaft member
fitted
raceway
peripheral surface
Prior art date
Application number
PCT/JP2014/076215
Other languages
French (fr)
Japanese (ja)
Inventor
信行 萩原
Original Assignee
日本精工株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本精工株式会社 filed Critical 日本精工株式会社
Priority to CN201480048779.2A priority Critical patent/CN105518321B/en
Priority to US15/026,800 priority patent/US9581192B2/en
Priority to EP14850592.8A priority patent/EP3054184B1/en
Publication of WO2015050143A1 publication Critical patent/WO2015050143A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/001—Hubs with roller-bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0078—Hubs characterised by the fixation of bearings
    • B60B27/0084—Hubs characterised by the fixation of bearings caulking to fix inner race
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/02—Dead axles, i.e. not transmitting torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/366—Tapered rollers, i.e. rollers generally shaped as truncated cones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/10—Type
    • B60B2380/14—Roller bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/60—Rolling elements
    • B60B2380/64—Specific shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/70—Arrangements
    • B60B2380/73—Double track
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/10—Force connections, e.g. clamping
    • F16C2226/12—Force connections, e.g. clamping by press-fit, e.g. plug-in
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/52—Positive connections with plastic deformation, e.g. caulking or staking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/20—Land vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings

Definitions

  • the present invention relates to a double row tapered roller bearing unit used for rotatably supporting a wheel with respect to a suspension device in a relatively heavy automobile such as a light truck and a large passenger car, and a method for manufacturing the same.
  • FIG. 9 shows a double-row tapered roller bearing unit used for rotationally supporting a drive wheel with respect to a suspension device in a relatively heavy automobile such as a light truck or a large passenger car.
  • This double-row tapered roller bearing unit includes an outer ring 1 that is an outer diameter side race ring member, a hub 2 that is an inner diameter side race ring member, and a plurality of tapered rollers 3.
  • the outer ring 1 includes double-row outer ring raceways 4 and 5 on the inner peripheral surface, and stationary flanges 6 on the outer peripheral surface for coupling and fixing to the knuckle of the suspension device.
  • the first outer ring raceway 4 located on the axially inner side which is one side in the axial direction and the second outer ring raceway 5 located on the outer side in the axial direction which is the other side in the axial direction Is formed by a partial conical surface inclined in a direction in which the diameter increases toward the direction away from each other.
  • “inside” in the axial direction means the center side in the width direction of the vehicle in the assembled state in the automobile, and is the right side in FIGS.
  • outside in the axial direction refers to the outside in the width direction of the vehicle, which is the left side of FIGS. 1 and 9 and the lower side of FIGS. 3 and 8.
  • the hub 2 is disposed concentrically with the outer ring 1 on the inner diameter side of the outer ring 1.
  • the hub 2 includes a plurality of rows of inner ring raceways 7 and 8 at the inner peripheral portion and the intermediate portion of the outer peripheral surface, and a portion projecting in the axial direction from the inner diameter side of the outer ring 1 at a portion closer to the outer end in the axial direction.
  • Rotation side flanges 9 for supporting and fixing each of them.
  • the first inner ring raceway 7 located on the inner side in the axial direction and the second inner ring raceway 8 located on the outer side in the axial direction have a larger diameter in the direction away from each other in the axial direction. It consists of a partial conical surface inclined in the direction.
  • the hub 2 includes an annular first inner ring 10 having a first inner ring raceway 7 formed on the outer peripheral surface, an annular second inner ring 11 having a second inner ring raceway 8 formed on the outer peripheral surface, and a rotation side flange 9.
  • the first inner ring raceway 7 (second inner ring raceway 8) is provided with a small flange portion provided at the small diameter end portion and a large diameter side end portion of the outer peripheral surface of the first inner ring 10 (second inner ring 11). It is provided between the buttocks.
  • the second inner ring 11 is externally fitted by an interference fit into the axially outer half of a cylindrical fitting surface portion 13 provided from the axially inner end portion to the intermediate portion of the outer peripheral surface of the hub body 12 by press fitting. .
  • the first inner ring 10 is externally fitted to the inner half of the fitting surface portion 13 in the axial direction by press-fitting.
  • the large-diameter side end surface of the first inner ring 10 is restrained by a caulking portion 15 formed by plastically deforming a cylindrical portion 14 provided at the axially inner end portion of the hub body 12 radially outward. ing.
  • first inner ring 10 and the second inner ring 11 are sandwiched from both sides in the axial direction by the step surface 16 and the caulking portion 15 existing at the axially outer end portion of the fitting surface portion 13 with respect to the hub body 12. Bonding is fixed.
  • a plurality of tapered rollers 3 are held by a cage 17 between the first outer ring raceway 4 and the first inner ring raceway 7 and between the second outer ring raceway 5 and the second inner ring raceway 8, respectively. It is arranged to roll freely in the state. Between the inner peripheral surface of the inner end portion in the axial direction of the outer ring 1 and the outer peripheral surface of the end portion on the large diameter side of the first inner ring 10 and the inner peripheral surface of the outer end portion in the axial direction of the outer ring 1 and the end portion on the large diameter side of the second inner ring 11. A combination seal ring 18 is assembled between each outer peripheral surface, and both axial ends of the cylindrical space in which the tapered rollers 3 are installed are closed. A spline hole 19 is provided at the center of the hub body 12 in the radial direction for inserting the tip of the drive shaft into spline engagement.
  • the first inner ring 10 When the hub 2 is assembled, as the caulking portion 15 is formed, the first inner ring 10 is elastically deformed so that the large-diameter end thereof is elastically larger than the small-diameter end. Along with this, the inclination angle of the first inner ring raceway 7 changes. Therefore, as described in Japanese Patent No. 4019548, the inclination of the first inner ring raceway 7 in the state before the caulking portion 15 is formed in consideration of the change in the inclination angle of the first inner ring raceway 7. It is necessary to adjust the angle. If such an adjustment is not made, the contact state between the rolling surface of the tapered roller 3 and the respective raceways 4, 5, 7, and 8 becomes irregular, and it is difficult to ensure the durability of the double-row tapered roller bearing unit.
  • the inclination angle of the first inner ring raceway 7 refers to the inclination angle of the first inner ring raceway 7 with respect to the central axis of the first inner ring 10.
  • the inclination angle of the second inner ring raceway 8 refers to the inclination angle of the second inner ring raceway 8 with respect to the central axis of the second inner ring 11.
  • an object of the present invention is to provide a structure of a double row tapered roller bearing unit capable of further improving durability and a manufacturing method for realizing such a double row tapered roller. Yes.
  • the double row tapered roller bearing unit of the present invention is An outer-diameter-side track ring member having a first outer ring raceway and a second outer ring raceway, each of which is constituted by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the inner peripheral surface;
  • An inner diameter side race ring member having a first inner ring raceway and a second outer ring raceway, each formed by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the outer peripheral surface;
  • a plurality of tapered rollers each provided between the first outer ring raceway and the first inner ring raceway and between the second outer ring raceway and the second inner ring raceway;
  • the inner diameter side race ring member includes a first inner ring having a first inner ring raceway formed on an outer peripheral surface, a second inner ring having a second inner ring raceway formed on
  • the second inner ring is externally fitted to the shaft member by press fitting, and the large-diameter side end surface of the first inner ring is suppressed by a caulking portion formed by plastic deformation at one axial end portion of the shaft member.
  • the first inner ring and the second inner ring are configured by being coupled and fixed to the shaft member.
  • the relationship is: ⁇ 1 + ⁇ a ( ⁇ X 1 ) + ⁇
  • the inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting.
  • a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member.
  • the outer diameter of the portion where the second inner ring is fitted to the shaft member before the first inner ring is fitted onto the shaft member is the portion of the outer peripheral surface of the shaft member where the second inner ring is fitted.
  • the outer diameter of the shaft member is larger than that before the second inner ring is externally fitted to the shaft member.
  • a spacer is sandwiched between the small-diameter side end surface of the first inner ring and the small-diameter side end surface of the second inner ring around the stepped portion. Moreover, it is preferable that the specifications of the first inner ring and the second inner ring are substantially equal.
  • a portion on which the first inner ring is fitted and a portion on which the second inner ring is fitted are configured by a single cylindrical surface that is continuous with each other.
  • the inner diameter dimension of the first inner ring in a state before the outer fitting is fitted by press-fitting is smaller than the inner diameter dimension of the second inner ring before the second inner ring is fitted on the shaft member by the press-fitting.
  • the first inner ring has an R chamfered portion at a continuous portion between the inner peripheral surface and the large-diameter end surface
  • the second inner ring has an R chamfered portion where the radius of curvature is larger than the radius of curvature of the R chamfered portion of the first inner ring, or an axial width dimension and a radial width dimension at a continuous portion between the inner peripheral surface and the large-diameter side end surface.
  • the shaft member has a rotation side flange for supporting and fixing the wheel at a portion adjacent to the other side in the axial direction of the portion where the second inner ring is fitted on the outer peripheral surface, and the second inner ring A cross-sectional arc shape that smoothly exists between the outer peripheral surface of the shaft member and the axial one side surface of the rotation side flange, which exists at a position facing the R chamfered portion or the C chamfered portion.
  • the corner R portion is a cross-sectional arc shape that smoothly exists between the outer peripheral surface of the shaft member and the axial one side surface of the rotation side flange, which exists at a position facing the R chamfered portion or the C chamfered portion.
  • the method for producing a double row tapered roller bearing unit of the present invention is a method for producing a double row tapered roller bearing unit having the above-described configuration, An inclination angle ⁇ 1 of the first inner ring raceway in a state before the first inner ring is fitted onto the shaft member by press fitting; An inclination angle ⁇ 2 of the second inner ring raceway in a state before the second inner ring is fitted over the shaft member by press fitting; A tilt angle reduction amount ⁇ a of the first inner ring raceway that is generated when the first inner ring is fitted onto the shaft member by press fitting; A tilt angle reduction amount ⁇ b of the second inner ring raceway that is generated when the second inner ring is fitted on the shaft member by press fitting; By adjusting the amount of increase ⁇ k of the inclination angle of the first inner ring race that is caused by forming the caulking portion, The inclination angle ⁇ 1 of the first inner ring raceway and the inclination angle ⁇ 2 of the second inner ring race in
  • the tilt angle reduction amount ⁇ a is adjusted by adjusting the press-fit allowance ⁇ X 1 of the first inner ring with respect to the shaft member, and the press-fit allowance ⁇ X 2 of the second inner ring with respect to the shaft member is set.
  • the inclination angle reduction amount ⁇ b can be adjusted.
  • the inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting.
  • a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member is The outer diameter of the part to be externally fitted before the first inner ring is externally fitted to the shaft member by press-fitting, the part of the outer peripheral surface of the shaft member to which the second inner ring is externally fitted, The press-fitting allowances ⁇ X 1 and ⁇ X 2 are respectively adjusted to be larger than the outer diameter dimension in a state before the second inner ring is externally fitted to the shaft member.
  • a spacer is sandwiched between the small-diameter side end face of the first inner ring and the small-diameter side end face of the second inner ring around the step portion.
  • the specifications of the first inner ring and the second inner ring are substantially equal.
  • a portion where the first inner ring is fitted and a portion where the second inner ring is fitted are a single cylindrical surface which is continuous with each other,
  • the inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting.
  • the press-fitting allowances ⁇ X 1 and ⁇ X 2 are respectively adjusted to be smaller.
  • an R chamfered portion is provided at a continuous portion between the inner peripheral surface of the first inner ring and the large-diameter end surface, and a first portion is provided at the continuous portion between the inner peripheral surface of the second inner ring and the large-diameter end surface.
  • a rotation side flange for supporting and fixing the wheel is provided in a portion adjacent to the other side in the axial direction of the portion fitting the second inner ring, and the R chamfered portion of the second inner ring Or the corner
  • angular area R of the circular arc section which exists in the position which opposes a C chamfering part, and makes these surfaces smoothly continue in the continuous part of the outer peripheral surface of the said shaft member and the axial direction one side surface of the said rotation side flange.
  • FIG. 1 is a cross-sectional view showing a first example of an embodiment of the present invention with some components omitted.
  • FIG. 2 is an enlarged view of part a in FIG.
  • FIG. 3 is a diagram showing a hub assembly method in the order of steps.
  • FIG. 4A is a diagram showing a change in the inclination angle of the first inner ring raceway caused by the assembly of the hub
  • FIG. 4B is a line showing a change in the inclination angle of the second inner ring raceway.
  • FIG. FIG. 5 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring and the amount of decrease in the inclination angle of the first inner ring raceway and the second inner ring raceway.
  • FIG. 6 is a diagram showing the relationship between the press-fit allowance of the first inner ring and the second inner ring, the amount of decrease in the inclination angle of the first inner ring track and the second inner ring track, and the amount of increase in the inclination angle of the first inner ring track.
  • FIG. 7 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring, the inclination angle of the first inner ring raceway and the second inner ring raceway after press fitting, and the amount of increase in the inclination angle of the first inner ring raceway is there.
  • FIG. 7 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring, the inclination angle of the first inner ring raceway and the second inner ring raceway after press fitting, and the amount of increase in the inclination angle of the first inner ring raceway is there.
  • FIG. 8 is a cross-sectional view showing the first inner ring, the second inner ring, and the hub body before being combined with each other, showing a second example of the embodiment of the present invention.
  • FIG. 9 is a sectional view showing an example of a conventional double-row tapered roller bearing unit for supporting a wheel.
  • the double-row tapered roller bearing unit for wheel support which is the object of this example, includes an outer ring 1, a hub 2a, and a plurality of tapered rollers 3, as in the conventional structure shown in FIG.
  • FIG. 1 shows the wheel support double-row tapered roller bearing unit according to the present embodiment.
  • the outer ring 1, a plurality of tapered rollers 3, a pair of cages 17 and a pair of combination seal rings 18 are part of the components. Is shown in a state where is omitted.
  • the outer ring 1 includes double row outer ring raceways 4 and 5 formed on the inner peripheral surface, and a stationary side flange 6 formed on the outer peripheral surface and coupled and fixed to the knuckle of the suspension device.
  • the first outer ring raceway 4 positioned on the inner side in the axial direction and the second outer ring raceway 5 positioned on the outer side in the axial direction increase in diameter toward the direction away from each other in the axial direction. It is comprised by the partial conical surface inclined in the direction which becomes.
  • the hub 2a is disposed concentrically with the outer ring 1 on the inner diameter side of the outer ring 1.
  • the hub 2a protrudes in the axial direction from the inner diameter side of the outer ring 1 at a portion closer to the outer end in the axial direction and the double-row inner ring raceways 7 and 8 formed respectively at the inner end and the intermediate portion of the outer peripheral surface.
  • a rotation-side flange 9 for supporting and fixing the wheel.
  • the first inner ring raceway 7 located on the inner side in the axial direction and the second inner ring raceway 8 located on the outer side in the axial direction have larger diameters as they go away from each other in the axial direction. It is comprised by the partial conical surface inclined in the direction which becomes.
  • the hub 2a includes an annular first inner ring 10 having a first inner ring raceway 7 formed on an outer peripheral surface, an annular second inner ring 11 having a second inner ring raceway 8 formed on an outer peripheral surface, and an annular shape used for preload adjustment.
  • the first inner ring raceway 7 (second inner ring raceway 8) is provided with a small flange portion provided at the small diameter end portion and a large diameter side end portion of the outer peripheral surface of the first inner ring 10 (second inner ring 11). It is provided in the part between the buttocks.
  • the second inner ring 11 is externally fitted with an interference fit by press-fitting into the outer half in the axial direction of a cylindrical fitting surface portion 13a provided from the inner end in the axial direction of the outer peripheral surface of the hub body 12a to the intermediate portion. It is fitted.
  • the first inner ring 10 is externally fitted with an interference fit by being press-fitted into the inner half of the fitting surface portion 13a in the axial direction.
  • the spacer 20 is sandwiched between the small diameter side end surface of the first inner ring 10 and the small diameter side end surface of the second inner ring 11.
  • the large-diameter side end face of the first inner ring 10 is held down by a caulking portion 15 formed by plastically deforming a cylindrical portion 14 provided at an axially inner end portion of the hub body 12a radially outward. . Accordingly, the first inner ring 10 and the second inner ring 11 and the spacer 20 are sandwiched from both sides in the axial direction by the step surface 16 and the caulking portion 15 existing at the outer end in the axial direction of the fitting surface portion 13a. It is fixedly coupled to 12a.
  • a plurality of tapered rollers 3 are held by a cage 17 between the first outer ring raceway 4 and the first inner ring raceway 7 and between the second outer ring raceway 5 and the second inner ring raceway 8, respectively. It is provided so that it can roll freely. Between the inner peripheral surface of the inner end portion in the axial direction of the outer ring 1 and the outer peripheral surface of the end portion on the large diameter side of the first inner ring 10 and the inner peripheral surface of the outer end portion in the axial direction of the outer ring 1 and the end portion on the large diameter side of the second inner ring 11. A combination seal ring 18 is assembled between each outer peripheral surface, and both axial ends of the cylindrical space in which the tapered rollers 3 are installed are closed. A spline hole 19 is provided at the center of the hub body 12 in the radial direction for inserting the tip of the drive shaft into spline engagement.
  • FIG. 3 (A) to 3 (F) show an assembling method of the hub 2a constituting the wheel bearing rolling bearing unit of this example in the order of steps.
  • the second inner ring 11 shown in FIG. 3A is connected to the axially outer end of the fitting surface portion 13a of the hub body 12a as shown in FIG. It fits by press-fitting from the inner side.
  • FIG. 3 (C) around the stepped portion 21 provided in the intermediate portion in the axial direction which is a portion adjacent to the inner side in the axial direction of the second inner ring 11 in the fitting surface portion 13a.
  • the seat 20 is externally fitted with a gap fit.
  • FIG. 3 (E) the first inner ring 10 shown in FIG.
  • 3 (D) is an axial inner end that is a portion adjacent to the inner side in the axial direction of the spacer 20 in the fitting surface portion 13a.
  • the outer portion is fitted with an interference fit.
  • FIG. 3 (F) a portion of the cylindrical portion 14 provided at the axially inner end portion of the hub body 12a that protrudes inward in the axial direction from the first inner ring 10 is plasticized toward the outer diameter side.
  • the caulking portion 15 is formed, and the caulking portion 15 suppresses the large-diameter side end surface (the axial inner end surface) of the first inner ring 10.
  • the relationship with the inclination angle ⁇ 1 of the first inner ring raceway 7 after the outer fitting is ⁇ 1 > ⁇ 1 as shown in the left half of FIG.
  • the relationship with the inclination angle ⁇ 2 of the second inner ring raceway 8 after the outer fitting is ⁇ 2 > ⁇ 2 as shown in FIG.
  • the press-fit allowance ⁇ X 1 (or ⁇ X 2 ) of the first inner ring 10 (or the second inner ring 11) with respect to the fitting surface portion 13a The relationship is specifically obtained by experiment or elastic FEM analysis, and is almost a straight line (proportional relationship) as shown in FIG.
  • the inclination angle of the first inner ring raceway 7 increases as the large diameter side end portion of the first inner ring 10 is elastically deformed in the diameter increasing direction. That is, the relationship between the inclination angle ⁇ 1 of the first inner ring raceway 7 before the caulking portion 15 is formed and the inclination angle ⁇ 1 of the first inner ring raceway 7 after the caulking portion 15 is formed is shown in FIG. As shown in the right half of (B), ⁇ 1 ⁇ 1 .
  • the inclination angle ⁇ 1 of the first inner ring raceway 7 and the second inner ring raceway in the state where the hub 2a is assembled that is, in the state where the caulking portion 15 is formed.
  • ⁇ 1 + ⁇ a ( ⁇ X 1 ) + ⁇ 2 ⁇ b ( ⁇ X 2 ) ⁇ k (4)
  • the first inner ring 10 and the second inner ring 11 are made of a material and in a state (free state) before the first inner ring 10 and the second inner ring 11 are fitted onto the fitting surface portion 13a by press fitting.
  • the specifications such as the shape and dimensions are substantially the same except for inevitable manufacturing errors.
  • the axial inner portion fitted around the first inner ring 10 the large diameter portion outside diameter in the state before fitted by press-fitting the first inner ring 10 is by D 1 22
  • the axially outer portion where the second inner ring 11 is externally fitted is a small diameter portion 23 whose outer diameter dimension is D 2 ( ⁇ D 1 ) before the second inner ring 11 is externally fitted by press-fitting.
  • ⁇ X 2 D 2 ⁇ d 2 of 10 within the range of the expression (6) ( ⁇ X 1 > ⁇ X 2 ).
  • the tilt angle decrease amount ⁇ a ( ⁇ X 1 ) is made larger than the tilt angle decrease amount ⁇ b ( ⁇ X 2 ) ( ⁇ a ( ⁇ X 1 )> ⁇ b ( ⁇ X 2 )), and the tilt angle decrease amount is increased.
  • ⁇ a ( ⁇ X 1), ⁇ b ( ⁇ X 2) the difference between ⁇ a ( ⁇ X 1) - ⁇ b and ([Delta] X 2), and a tilt angle increase amount .delta..theta k, by substantially equal, (5 ) Is satisfied.
  • the first inner ring 10 and the second inner ring 11 are substantially the same in terms of material, shape, dimensions, and the like. For this reason, it is easy to ensure quality and productivity and reduce costs based on the fact that a device for finishing grinding can be used in common for the first inner ring raceway 7 and the second inner ring raceway 8. Further, the spacer 20 is sandwiched between the small-diameter side end surface of the first inner ring 10 and the small-diameter side end surface of the second inner ring 11, and the portion of the fitting surface portion 13a located on the inner diameter side of the spacer 20 is A stepped portion 21 is provided. For this reason, it is possible to prevent the first inner ring 10 or the second inner ring 11 from being externally fitted to the step portion 21 and to prevent adverse effects such as variations in the press-fitting allowance ⁇ X 1 or ⁇ X 2. .
  • the present invention can also be applied to a double-row tapered roller bearing unit for supporting a wheel for a driven wheel or a double-row tapered roller bearing unit other than for supporting a wheel.
  • the present invention can also be applied to a double-row tapered roller bearing unit in which the outer diameter side race ring member rotates in use and the inner diameter side race ring member does not rotate.
  • the inclination angle ⁇ 2 of the track can be made different from each other, and the appropriate range of the inclination angle ⁇ 1 of the first inner ring track and the inclination angle ⁇ 2 of the second inner ring track in the state after the caulking portion is formed.
  • the appropriate range can be different from each other.
  • FIG. 8 shows a second example of the embodiment of the present invention.
  • the radially inner end portion (step surface 16) of the inner side surface of the rotation side flange 9 and the fitting surface portion 13 The radius of curvature of the corner R portion 24a existing in the continuous portion is larger than the radius of curvature of the corner R portion 24 of the hub body 12a according to the first example of the embodiment.
  • the radius of curvature of the R chamfered portion 26a that is located at the continuous portion between the inner peripheral surface of the second inner ring 11a and the large-diameter side end surface that is disposed at a position facing the corner R portion 24a is also the same as that of the embodiment. It is larger than the radius of curvature of the R chamfered portion 26 of the second inner ring 11 in the first example. This prevents the R chamfered portion 26 a from interfering with the corner R portion 24 a and preventing the large-diameter side end surface of the second inner ring 11 a from coming into contact with the stepped surface 16.
  • the radius of curvature of the R chamfered portion 26a of the second inner ring 11a is larger than the radius of curvature of the R chamfered portion 25 existing at the continuous portion between the inner peripheral surface of the first inner ring 10 and the large diameter side end surface. It is getting bigger. That is, at least in this respect, the specifications of the first inner ring 10 and the specifications of the second inner ring 11a are different from each other.
  • the portion of the fitting surface portion 13 that externally fits the first inner ring 10 and the portion that externally fits the second inner ring 11a are mutually connected.
  • the inner diameter dimension d 1 in the state before the outer fitting by the interference fit.
  • the inclination angle reduction amount ⁇ a ( ⁇ X 1 ) of the first inner ring raceway 7 is larger than the inclination angle reduction amount ⁇ b ( ⁇ X 2 ) of the second inner ring raceway 8 ( ⁇ a ( ⁇ X 1 )> ⁇ b ( with [Delta] X 2) and), these inclination angles decrease ⁇ a ( ⁇ X 1), ⁇ b ( ⁇ X 2) the difference between ⁇ a ( ⁇ X 1) and - ⁇ b ( ⁇ X 2), the inclination angle increases the amount .delta..theta By making k substantially equal, the relationship of equation (5) is satisfied.
  • the fitting surface portion 13 is a single cylindrical surface, and a step portion serving as a stress concentration source is provided at the axial intermediate portion of the fitting surface portion 13. Therefore, as compared with the case of the first example of the embodiment, it is easy to design to ensure the strength of the hub main body 12b, and it is easy to ensure the productivity of the hub main body 12b and reduce the cost. Other configurations and operations are the same as those of the first example of the embodiment.
  • the R chamfered portion 26a of the second inner ring 11a can be changed to a C chamfered portion.
  • the axial width dimension and the radial width dimension of the C chamfered portion are set to the curvature radius of the R chamfered portion 25 of the first inner ring 10 (the curvature of the R chamfered portion 26 of the second inner ring 11 of the first example of the embodiment).
  • the radius of curvature of the corner R portion 24a existing at the base portion of the rotation side flange 9 can be increased correspondingly, and the strength of the base portion can be improved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

Provided are: a structure for a double-row tapered roller bearing unit, the structure enabling the satisfactory contact between the rolling surfaces of double-row tapered rollers and both a first inner ring raceway (7) and a second inner ring raceway (8) to be ensured; and a method for manufacturing the double-row tapered roller bearing unit. The following adjustments are performed: the adjustment of both the tilt angle (θ1) of the first inner ring raceway (7) and the tilt angle (θ2) of the second inner ring raceway (8) before a first inner ring (10) and a second inner ring (11) are press-fitted over the fitting surface section (13a) of a hub body (12a); the adjustment of both the amount of decrease (δθa) in the tilt angle of the first inner ring raceway (7) and the amount of decrease (δθb) in the tilt angle of the second inner ring raceway (8), the decreases being caused by the press-fitting of the first inner ring (10) and the second inner ring (11) over the fitting surface section (13a); and the adjustment of the amount of increase (δθk) in the tilt angle of the first inner ring (7), the increase being caused by the formation of a crimped section (15). As a result of the above-described adjustments, the tilt angle (φ1) of the first inner ring raceway (7) and the tilt angle (Θ2) of the second inner ring raceway (8), which are measured after the formation of the crimped section (15), are brought into respective appropriate ranges.

Description

複列円すいころ軸受ユニットおよびその製造方法Double-row tapered roller bearing unit and manufacturing method thereof
　本発明は、小型トラック、大型乗用車などの、比較的重量が嵩む自動車において、車輪を懸架装置に対して回転自在に支持するために用いられる、複列円すいころ軸受ユニットおよびその製造方法に関する。 BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a double row tapered roller bearing unit used for rotatably supporting a wheel with respect to a suspension device in a relatively heavy automobile such as a light truck and a large passenger car, and a method for manufacturing the same.
　図９は、小型トラック、大型乗用車などの、比較的重量が嵩む自動車において、駆動輪を懸架装置に対して回転支持するために用いられる、複列円すいころ軸受ユニットを示している。この複列円すいころ軸受ユニットは、外径側軌道輪部材である外輪１と、内径側軌道輪部材であるハブ２と、複数個の円すいころ３とを備える。 FIG. 9 shows a double-row tapered roller bearing unit used for rotationally supporting a drive wheel with respect to a suspension device in a relatively heavy automobile such as a light truck or a large passenger car. This double-row tapered roller bearing unit includes an outer ring 1 that is an outer diameter side race ring member, a hub 2 that is an inner diameter side race ring member, and a plurality of tapered rollers 3.
　外輪１は、内周面に複列の外輪軌道４、５を、外周面に懸架装置のナックルに結合固定するための静止側フランジ６を、それぞれ備える。複列の外輪軌道４、５のうち、軸方向片側である軸方向内側に位置する第１外輪軌道４と、軸方向他側である軸方向外側に位置する第２外輪軌道５は、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した、部分円すい面により構成される。なお、軸方向に関して「内」とは、自動車への組み付け状態で車両の幅方向中央側をいい、図１および図９においては右側、図３および図８においては上側である。一方、軸方向に関して「外」とは、車両の幅方向外側をいい、図１および図９の左側、図３および図８の下側である。 The outer ring 1 includes double-row outer ring raceways 4 and 5 on the inner peripheral surface, and stationary flanges 6 on the outer peripheral surface for coupling and fixing to the knuckle of the suspension device. Among the double-row outer ring raceways 4 and 5, the first outer ring raceway 4 located on the axially inner side which is one side in the axial direction and the second outer ring raceway 5 located on the outer side in the axial direction which is the other side in the axial direction Is formed by a partial conical surface inclined in a direction in which the diameter increases toward the direction away from each other. Note that “inside” in the axial direction means the center side in the width direction of the vehicle in the assembled state in the automobile, and is the right side in FIGS. 1 and 9 and the upper side in FIGS. 3 and 8. On the other hand, “outside” in the axial direction refers to the outside in the width direction of the vehicle, which is the left side of FIGS. 1 and 9 and the lower side of FIGS. 3 and 8.
　ハブ２は、外輪１の内径側に、外輪１と同心に配置されている。ハブ２は、外周面のうち、軸方向内端部および中間部に複列の内輪軌道７、８を、軸方向外端寄り部分で外輪１の内径側から軸方向に突出した部分に、車輪を支持固定するための回転側フランジ９を、それぞれ備える。複列の内輪軌道７、８のうち、軸方向内側に位置する第１内輪軌道７と、軸方向外側に位置する第２内輪軌道８は、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面により構成される。 The hub 2 is disposed concentrically with the outer ring 1 on the inner diameter side of the outer ring 1. The hub 2 includes a plurality of rows of inner ring raceways 7 and 8 at the inner peripheral portion and the intermediate portion of the outer peripheral surface, and a portion projecting in the axial direction from the inner diameter side of the outer ring 1 at a portion closer to the outer end in the axial direction. Rotation side flanges 9 for supporting and fixing each of them. Of the double-row inner ring raceways 7 and 8, the first inner ring raceway 7 located on the inner side in the axial direction and the second inner ring raceway 8 located on the outer side in the axial direction have a larger diameter in the direction away from each other in the axial direction. It consists of a partial conical surface inclined in the direction.
　ハブ２は、外周面に第１内輪軌道７が形成された円環状の第１内輪１０と、外周面に第２内輪軌道８が形成された円環状の第２内輪１１と、回転側フランジ９が一体に形成された、軸部材であるハブ本体１２とにより構成される。第１内輪軌道７（第２内輪軌道８）は、第１内輪１０（第２内輪１１）の外周面の小径側端部に設けられた小鍔部と大径側端部に設けられた大鍔部との間に設けられている。第２内輪１１は、ハブ本体１２の外周面の軸方向内端部から中間部にかけて設けられた円筒状の嵌合面部１３の軸方向外半部に、圧入により締り嵌めで外嵌されている。第１内輪１０は、嵌合面部１３の軸方向内半部に、圧入により締り嵌めで外嵌されている。第１内輪１０の大径側端面は、ハブ本体１２の軸方向内端部に設けられた円筒部１４を、径方向外方に塑性変形させることにより形成された、かしめ部１５により抑えつけられている。したがって、第１内輪１０および第２内輪１１は、嵌合面部１３の軸方向外端部に存在する段差面１６とかしめ部１５により軸方向両側から挟持された状態で、ハブ本体１２に対して結合固定されている。 The hub 2 includes an annular first inner ring 10 having a first inner ring raceway 7 formed on the outer peripheral surface, an annular second inner ring 11 having a second inner ring raceway 8 formed on the outer peripheral surface, and a rotation side flange 9. Are integrally formed with a hub body 12 as a shaft member. The first inner ring raceway 7 (second inner ring raceway 8) is provided with a small flange portion provided at the small diameter end portion and a large diameter side end portion of the outer peripheral surface of the first inner ring 10 (second inner ring 11). It is provided between the buttocks. The second inner ring 11 is externally fitted by an interference fit into the axially outer half of a cylindrical fitting surface portion 13 provided from the axially inner end portion to the intermediate portion of the outer peripheral surface of the hub body 12 by press fitting. . The first inner ring 10 is externally fitted to the inner half of the fitting surface portion 13 in the axial direction by press-fitting. The large-diameter side end surface of the first inner ring 10 is restrained by a caulking portion 15 formed by plastically deforming a cylindrical portion 14 provided at the axially inner end portion of the hub body 12 radially outward. ing. Therefore, the first inner ring 10 and the second inner ring 11 are sandwiched from both sides in the axial direction by the step surface 16 and the caulking portion 15 existing at the axially outer end portion of the fitting surface portion 13 with respect to the hub body 12. Bonding is fixed.
　円すいころ３は、第１外輪軌道４と第１内輪軌道７との間と、第２外輪軌道５と第２内輪軌道８との間とに、それぞれ複数個ずつ、保持器１７により保持された状態で転動自在に配置されている。外輪１の軸方向内端部内周面と第１内輪１０の大径側端部外周面との間、および、外輪１の軸方向外端部内周面と第２内輪１１の大径側端部外周面との間には、それぞれ組み合わせシールリング１８が組み付けられ、円すいころ３を設置した円筒状空間の軸方向両端開口が塞がれている。ハブ本体１２の径方向中心部には、駆動軸の先端部を挿入してスプライン係合させるためのスプライン孔１９が設けられている。 A plurality of tapered rollers 3 are held by a cage 17 between the first outer ring raceway 4 and the first inner ring raceway 7 and between the second outer ring raceway 5 and the second inner ring raceway 8, respectively. It is arranged to roll freely in the state. Between the inner peripheral surface of the inner end portion in the axial direction of the outer ring 1 and the outer peripheral surface of the end portion on the large diameter side of the first inner ring 10 and the inner peripheral surface of the outer end portion in the axial direction of the outer ring 1 and the end portion on the large diameter side of the second inner ring 11. A combination seal ring 18 is assembled between each outer peripheral surface, and both axial ends of the cylindrical space in which the tapered rollers 3 are installed are closed. A spline hole 19 is provided at the center of the hub body 12 in the radial direction for inserting the tip of the drive shaft into spline engagement.
　ハブ２を組み立てる際には、かしめ部１５を形成することに伴って、第１内輪１０が、その大径側端部が小径側端部よりも弾性的に大きく拡径するように弾性変形することに伴い、第１内輪軌道７の傾斜角度が変化する。したがって、日本国特許第４０１９５４８号公報に記載されているように、第１内輪軌道７の傾斜角度の変化を考慮して、かしめ部１５を形成する前の状態での第１内輪軌道７の傾斜角度を調整する必要がある。このような調整がなされないと、円すいころ３の転動面とそれぞれの軌道４、５、７、８との当接状態が不正規になり、複列円すいころ軸受ユニットの耐久性確保が難しくなる可能性がある。なお、第１内輪軌道７の傾斜角度とは、第１内輪軌道７の、第１内輪１０の中心軸に対する傾斜角度をいう。第２内輪軌道８の傾斜角度とは、第２内輪軌道８の、第２内輪１１の中心軸に対する傾斜角度をいう。 When the hub 2 is assembled, as the caulking portion 15 is formed, the first inner ring 10 is elastically deformed so that the large-diameter end thereof is elastically larger than the small-diameter end. Along with this, the inclination angle of the first inner ring raceway 7 changes. Therefore, as described in Japanese Patent No. 4019548, the inclination of the first inner ring raceway 7 in the state before the caulking portion 15 is formed in consideration of the change in the inclination angle of the first inner ring raceway 7. It is necessary to adjust the angle. If such an adjustment is not made, the contact state between the rolling surface of the tapered roller 3 and the respective raceways 4, 5, 7, and 8 becomes irregular, and it is difficult to ensure the durability of the double-row tapered roller bearing unit. There is a possibility. The inclination angle of the first inner ring raceway 7 refers to the inclination angle of the first inner ring raceway 7 with respect to the central axis of the first inner ring 10. The inclination angle of the second inner ring raceway 8 refers to the inclination angle of the second inner ring raceway 8 with respect to the central axis of the second inner ring 11.
　しかしながら、第１内輪軌道７の傾斜角度の変化を考慮して、かしめ部１５を形成する前の状態での第１内輪軌道７の傾斜角度を調整したのみでは、ハブ２を組み立てた後における、第１内輪軌道７の傾斜角度と第２内輪軌道８の傾斜角度を適正範囲内とし、特に、これらの傾斜角度を同一とするには十分ではない。このように、複列円すいころ軸受ユニットの耐久性を向上させる観点からは、いまだ改良の余地がある。 However, in consideration of the change in the inclination angle of the first inner ring raceway 7, only by adjusting the inclination angle of the first inner ring raceway 7 in the state before the caulking portion 15 is formed, after the hub 2 is assembled, It is not sufficient to make the inclination angle of the first inner ring raceway 7 and the inclination angle of the second inner ring raceway 8 within an appropriate range, and in particular, to make these inclination angles the same. Thus, there is still room for improvement from the viewpoint of improving the durability of the double row tapered roller bearing unit.
特許４０１９５４８号公報Japanese Patent No. 4019548
　本発明は、このような事情に鑑み、耐久性をより向上させることができる複列円すいころ軸受ユニットの構造およびこのような複列円すいころを実現するための製造方法を提供することを目的としている。 In view of such circumstances, an object of the present invention is to provide a structure of a double row tapered roller bearing unit capable of further improving durability and a manufacturing method for realizing such a double row tapered roller. Yes.
　本発明の複列円すいころ軸受ユニットは、
　内周面に、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面によりそれぞれ構成された、第１外輪軌道および第２外輪軌道を有する外径側軌道輪部材と、
　外周面に、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面によりそれぞれ構成された、第１内輪軌道および第２外輪軌道を有する内径側軌道輪部材と、
　第１外輪軌道と第１内輪軌道との間、および、第２外輪軌道と第２内輪軌道との間に、それぞれ複数個ずつ転動自在に設けられた円すいころと、
を備え、
　前記内径側軌道輪部材は、外周面に第１内輪軌道が形成された第１内輪と、外周面に第２内輪軌道が形成された第２内輪と、軸部材とを備え、第１内輪および第２内輪が、前記軸部材に圧入により外嵌され、かつ、該軸部材の軸方向片端部に塑性変形により形成されたかしめ部により、第１内輪の大径側端面を抑え付けることで、第１内輪および第２内輪が前記軸部材に結合固定されることにより構成される。 The double row tapered roller bearing unit of the present invention is
An outer-diameter-side track ring member having a first outer ring raceway and a second outer ring raceway, each of which is constituted by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the inner peripheral surface;
An inner diameter side race ring member having a first inner ring raceway and a second outer ring raceway, each formed by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the outer peripheral surface;
A plurality of tapered rollers each provided between the first outer ring raceway and the first inner ring raceway and between the second outer ring raceway and the second inner ring raceway;
With
The inner diameter side race ring member includes a first inner ring having a first inner ring raceway formed on an outer peripheral surface, a second inner ring having a second inner ring raceway formed on an outer peripheral surface, and a shaft member. The second inner ring is externally fitted to the shaft member by press fitting, and the large-diameter side end surface of the first inner ring is suppressed by a caulking portion formed by plastic deformation at one axial end portion of the shaft member. The first inner ring and the second inner ring are configured by being coupled and fixed to the shaft member.
　特に、本発明の複列円すいころ軸受ユニットでは、
　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪軌道の傾斜角度θ1と、
　前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪軌道の傾斜角度θ2と、
　前記軸部材に第１内輪を圧入により外嵌することに伴って生じる第１内輪軌道の傾斜角度減少量δθaと、
　前記軸部材に第２内輪を圧入により外嵌することに伴って生じる第２内輪軌道の傾斜角度減少量δθbと、
　前記かしめ部を形成することに伴って生じる第１内輪軌道の傾斜角度増大量δθkと、
　前記軸部材に対する第１内輪の圧入代ΔＸ1と、
　前記軸部材に対する第２内輪の圧入代ΔＸ2と、
の関係が、次式：
　－θ1＋δθa（ΔＸ1）＋θ2－δθb（ΔＸ2）＝δθk　
を満たし、 
　前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ1と第２内輪軌道の傾斜角度Θ2とが、それぞれの適正範囲内に収められていることを特徴とする。なお、好ましくは、前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ1と第２内輪軌道の傾斜角度Θ2とが、それぞれの適正範囲内で実質的に同一となる。 In particular, in the double row tapered roller bearing unit of the present invention,
An inclination angle θ 1 of the first inner ring raceway in a state before the first inner ring is fitted onto the shaft member by press fitting;
An inclination angle θ 2 of the second inner ring raceway in a state before the second inner ring is fitted over the shaft member by press fitting;
A tilt angle reduction amount δθ a of the first inner ring raceway that is generated when the first inner ring is fitted onto the shaft member by press fitting;
A tilt angle reduction amount δθ b of the second inner ring raceway that is generated when the second inner ring is fitted on the shaft member by press fitting;
A tilt angle increase amount δθ k of the first inner ring raceway that is generated when the caulking portion is formed, and
A pressure allowance ΔX 1 of the first inner ring with respect to the shaft member;
A press-fitting allowance ΔX 2 of the second inner ring with respect to the shaft member;
The relationship is:
−θ 1 + δθ a (ΔX 1 ) + θ 2 −δθ b (ΔX 2 ) = δθ k
The filling,
The inclination angle φ 1 of the first inner ring raceway and the inclination angle Θ 2 of the second inner ring raceway in a state after the caulking portion is formed are within the appropriate ranges. Preferably, the inclination angle φ 1 of the first inner ring raceway and the inclination angle Θ 2 of the second inner ring raceway in the state after forming the caulking portion are substantially the same within the appropriate ranges. .
　本発明の複列円すいころ軸受ユニットの一態様では、
　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法と、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法とが実質的に等しく、
　前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分との間に段部が設けられ、前記軸部材の外周面のうちの第１内輪が外嵌される部分の、該軸部材に第１内輪を圧入により外嵌する前の状態での外径寸法が、前記軸部材の外周面のうちの第２内輪が外嵌される部分の、該軸部材に第２内輪を圧入により外嵌する前の状態での外径寸法よりも大きくなっている。 In one aspect of the double row tapered roller bearing unit of the present invention,
The inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting. Is substantially equal to
Of the outer peripheral surface of the shaft member, a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member. The outer diameter of the portion where the second inner ring is fitted to the shaft member before the first inner ring is fitted onto the shaft member is the portion of the outer peripheral surface of the shaft member where the second inner ring is fitted. The outer diameter of the shaft member is larger than that before the second inner ring is externally fitted to the shaft member.
　この場合、前記段部の周囲で、第１内輪の小径側端面と第２内輪の小径側端面との間に間座が挟持されていることが好ましい。また、第１内輪および第２内輪の諸元が実質的に等しくなっていることが好ましい。 In this case, it is preferable that a spacer is sandwiched between the small-diameter side end surface of the first inner ring and the small-diameter side end surface of the second inner ring around the stepped portion. Moreover, it is preferable that the specifications of the first inner ring and the second inner ring are substantially equal.
　本発明の複列円すいころ軸受ユニットの別態様では、
前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分とが互いに連続した単一円筒面により構成されており、前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法が、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法よりも小さくなっている。 In another aspect of the double row tapered roller bearing unit of the present invention,
Of the outer peripheral surface of the shaft member, a portion on which the first inner ring is fitted and a portion on which the second inner ring is fitted are configured by a single cylindrical surface that is continuous with each other. The inner diameter dimension of the first inner ring in a state before the outer fitting is fitted by press-fitting is smaller than the inner diameter dimension of the second inner ring before the second inner ring is fitted on the shaft member by the press-fitting.
　この態様では、好ましくは、
　第１内輪が、内周面と大径側端面との連続部にＲ面取り部を有し、
　第２内輪が、内周面と大径側端面との連続部に、曲率半径が第１内輪のＲ面取り部の曲率半径よりも大きいＲ面取り部、または、軸方向幅寸法および径方向幅寸法が第１内輪のＲ面取り部の曲率半径よりも大きいＣ面取り部を有し、
　前記軸部材は、外周面のうち、第２内輪が外嵌される部分の軸方向他側に隣接する部分に、車輪を支持固定するための回転側フランジを有し、かつ、第２内輪のＲ面取り部またはＣ面取り部と対向する位置に存在する、前記軸部材の外周面と前記回転側フランジの軸方向片側面との連続部に、これらの面同士を滑らかに連続させる断面円弧形の隅Ｒ部を有する。 In this aspect, preferably
The first inner ring has an R chamfered portion at a continuous portion between the inner peripheral surface and the large-diameter end surface,
The second inner ring has an R chamfered portion where the radius of curvature is larger than the radius of curvature of the R chamfered portion of the first inner ring, or an axial width dimension and a radial width dimension at a continuous portion between the inner peripheral surface and the large-diameter side end surface. Has a C chamfer that is larger than the radius of curvature of the R chamfer of the first inner ring,
The shaft member has a rotation side flange for supporting and fixing the wheel at a portion adjacent to the other side in the axial direction of the portion where the second inner ring is fitted on the outer peripheral surface, and the second inner ring A cross-sectional arc shape that smoothly exists between the outer peripheral surface of the shaft member and the axial one side surface of the rotation side flange, which exists at a position facing the R chamfered portion or the C chamfered portion. The corner R portion.
　本発明の複列円すいころ軸受ユニットの製造方法は、上述した構成を備える複列円すいころ軸受ユニットの製造方法であって、
　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪軌道の傾斜角度θ1と、
　前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪軌道の傾斜角度θ2と、
　前記軸部材に第１内輪を圧入により外嵌することに伴って生じる第１内輪軌道の傾斜角度減少量δθaと、
　前記軸部材に第２内輪を圧入により外嵌することに伴って生じる第２内輪軌道の傾斜角度減少量δθbと、
　前記かしめ部を形成することに伴って生じる第１内輪軌道の傾斜角度増大量δθkとを調整することにより、
　前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ1と第２内輪軌道の傾斜角度Θ2とを、それぞれの適正範囲内に収めることを特徴とする。なお、好ましくは、前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ1と第２内輪軌道の傾斜角度Θ2とを、それぞれの適正範囲内で実質的に同一とする。 The method for producing a double row tapered roller bearing unit of the present invention is a method for producing a double row tapered roller bearing unit having the above-described configuration,
An inclination angle θ 1 of the first inner ring raceway in a state before the first inner ring is fitted onto the shaft member by press fitting;
An inclination angle θ 2 of the second inner ring raceway in a state before the second inner ring is fitted over the shaft member by press fitting;
A tilt angle reduction amount δθ a of the first inner ring raceway that is generated when the first inner ring is fitted onto the shaft member by press fitting;
A tilt angle reduction amount δθ b of the second inner ring raceway that is generated when the second inner ring is fitted on the shaft member by press fitting;
By adjusting the amount of increase δθ k of the inclination angle of the first inner ring race that is caused by forming the caulking portion,
The inclination angle φ 1 of the first inner ring raceway and the inclination angle Θ 2 of the second inner ring race in a state after the caulking portion is formed are within respective appropriate ranges. Preferably, the inclination angle φ 1 of the first inner ring raceway and the inclination angle Θ 2 of the second inner ring raceway in the state after forming the caulking portion are substantially the same within the appropriate ranges. .
　この場合、好ましくは、前記傾斜角度θ1と前記傾斜角度θ2とを実質的に等しくし、次式：
　δθa（ΔＸ1）－δθb（ΔＸ2）＝δθk　
を満たすように、前記調整を行う。 In this case, preferably, the inclination angle θ 1 and the inclination angle θ 2 are substantially equal, and the following formula:
δθ a (ΔX 1 ) −δθ b (ΔX 2 ) = δθ k
The adjustment is performed so as to satisfy
　より具体的には、前記軸部材に対する前記第１内輪の圧入代ΔＸ1を調整することにより、前記傾斜角度減少量δθaを調整し、前記軸部材に対する前記第２内輪の圧入代ΔＸ2を調整することにより、前記傾斜角度減少量δθbを調整することができる。 More specifically, the tilt angle reduction amount δθ a is adjusted by adjusting the press-fit allowance ΔX 1 of the first inner ring with respect to the shaft member, and the press-fit allowance ΔX 2 of the second inner ring with respect to the shaft member is set. By adjusting, the inclination angle reduction amount δθ b can be adjusted.
　本発明の複列円すいころ軸受ユニットの製造方法の一態様では、
前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法と、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法とを実質的に等しくし、
　前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分との間に段部を設け、前記軸部材の外周面のうちの第１内輪が外嵌される部分の、該軸部材に第１内輪を圧入により外嵌する前の状態での外径寸法を、前記軸部材の外周面のうちの第２内輪が外嵌される部分の、該軸部材に第２内輪を圧入により外嵌する前の状態での外径寸法よりも大きくして、前記圧入代ΔＸ１、ΔＸ２をそれぞれ調整する。 In one aspect of the manufacturing method of the double row tapered roller bearing unit of the present invention,
The inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting. And substantially equal,
Of the outer peripheral surface of the shaft member, a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member is The outer diameter of the part to be externally fitted before the first inner ring is externally fitted to the shaft member by press-fitting, the part of the outer peripheral surface of the shaft member to which the second inner ring is externally fitted, The press-fitting allowances ΔX 1 and ΔX 2 are respectively adjusted to be larger than the outer diameter dimension in a state before the second inner ring is externally fitted to the shaft member.
　この場合、好ましくは、前記段部の周囲で、第１内輪の小径側端面と第２内輪の小径側端面との間に間座を挟持する。また、好ましくは、第１内輪および第２内輪の諸元を実質的に等しくする。 In this case, preferably, a spacer is sandwiched between the small-diameter side end face of the first inner ring and the small-diameter side end face of the second inner ring around the step portion. Preferably, the specifications of the first inner ring and the second inner ring are substantially equal.
　一方、本発明の複列円すいころ軸受ユニットの製造方法の別態様では、
前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分とを互いに連続した単一円筒面とし、
　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法を、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法よりも小さくして、前記圧入代ΔＸ１、ΔＸ２をそれぞれ調整する。 On the other hand, in another aspect of the manufacturing method of the double row tapered roller bearing unit of the present invention,
Of the outer peripheral surface of the shaft member, a portion where the first inner ring is fitted and a portion where the second inner ring is fitted are a single cylindrical surface which is continuous with each other,
The inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting. The press-fitting allowances ΔX 1 and ΔX 2 are respectively adjusted to be smaller.
　この場合、好ましくは、第１内輪の内周面と大径側端面との連続部に、Ｒ面取り部を設け、第２内輪の内周面と大径側端面との連続部に、第１内輪のＲ面取り部の曲率半径よりも大きな曲率半径を有するＲ面取り部、または、第１内輪のＲ面取り部の曲率半径よりも大きい、軸方向幅寸法および径方向幅寸法を有するＣ面取り部を設けると共に、
　前記軸部材の外周面のうち、第２内輪を外嵌する部分の軸方向他側に隣接する部分に、車輪を支持固定するための回転側フランジを設け、かつ、第２内輪のＲ面取り部またはＣ面取り部と対向する位置に存在する、前記軸部材の外周面と前記回転側フランジの軸方向片側面との連続部に、これらの面同士を滑らかに連続させる断面円弧形の隅Ｒ部を設ける。 In this case, preferably, an R chamfered portion is provided at a continuous portion between the inner peripheral surface of the first inner ring and the large-diameter end surface, and a first portion is provided at the continuous portion between the inner peripheral surface of the second inner ring and the large-diameter end surface. An R chamfered portion having a radius of curvature greater than the radius of curvature of the R chamfered portion of the inner ring, or a C chamfered portion having an axial width dimension and a radial width dimension greater than the radius of curvature of the R chamfered portion of the first inner ring. While providing
Of the outer peripheral surface of the shaft member, a rotation side flange for supporting and fixing the wheel is provided in a portion adjacent to the other side in the axial direction of the portion fitting the second inner ring, and the R chamfered portion of the second inner ring Or the corner | angular area R of the circular arc section which exists in the position which opposes a C chamfering part, and makes these surfaces smoothly continue in the continuous part of the outer peripheral surface of the said shaft member and the axial direction one side surface of the said rotation side flange. Provide a part.
　本発明の複列円すいころ軸受ユニットおよびその製造方法では、かしめ部の形成に伴う第１内輪軌道の傾斜角度増大量δθkだけでなく、軸部材に第１内輪および第２内輪を圧入により外嵌することに伴う第１内輪軌道の傾斜角度減少量δθaおよび第２内輪軌道の傾斜角度減少量δθbをも考慮して、前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ１および第２内輪軌道の傾斜角度Θ2の調整を行うため、これらの傾斜角度φ1、Θ2を、それぞれの適正範囲の中央値（最も理想的な値）に十分に近づけることができる。この結果、複列の内輪軌道および複列の外輪軌道と円すいころの転動面との当接状態を向上させることができる。これにより、複列円すいころ軸受ユニットの耐久性をより向上させることができる。 In the double-row tapered roller bearing unit and the manufacturing method thereof according to the present invention, not only the inclination angle increase amount δθ k of the first inner ring raceway due to the formation of the caulking portion but also the first inner ring and the second inner ring are inserted into the shaft member by press fitting. the inclination angle decrease .delta..theta b tilt angle reduction .delta..theta a and the second inner ring raceway of the first inner ring raceway with to fit also in consideration, the first inner ring raceway in the state after forming the crimped portion In order to adjust the inclination angle φ 1 and the inclination angle Θ 2 of the second inner ring raceway, these inclination angles φ 1 and Θ 2 are sufficiently close to the median value (the most ideal value) of the appropriate range. Can do. As a result, the contact state of the double row inner ring raceway and the double row outer ring raceway with the rolling surface of the tapered roller can be improved. Thereby, durability of a double row tapered roller bearing unit can be improved more.
図１は、本発明の実施の形態の第１例を、一部の部品を省略した状態で示す断面図である。FIG. 1 is a cross-sectional view showing a first example of an embodiment of the present invention with some components omitted. 図２は、図１のａ部拡大図である。FIG. 2 is an enlarged view of part a in FIG. 図３は、ハブの組立方法を工程順に示す図である。FIG. 3 is a diagram showing a hub assembly method in the order of steps. 図４（Ａ）は、ハブの組み立てに伴って生じる、第１内輪軌道の傾斜角度の変化を示す線図であり、図４（Ｂ）は、第２内輪軌道の傾斜角度の変化を示す線図である。FIG. 4A is a diagram showing a change in the inclination angle of the first inner ring raceway caused by the assembly of the hub, and FIG. 4B is a line showing a change in the inclination angle of the second inner ring raceway. FIG. 図５は、第１内輪および第２内輪の圧入代と、第１内輪軌道および第２内輪軌道の傾斜角度減少量との関係を示す線図である。FIG. 5 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring and the amount of decrease in the inclination angle of the first inner ring raceway and the second inner ring raceway. 図６は、第１内輪および第２内輪の圧入代と、第１内輪軌道および第２内輪軌道の傾斜角度減少量と、第１内輪軌道の傾斜角度増大量との関係を示す線図である。FIG. 6 is a diagram showing the relationship between the press-fit allowance of the first inner ring and the second inner ring, the amount of decrease in the inclination angle of the first inner ring track and the second inner ring track, and the amount of increase in the inclination angle of the first inner ring track. . 図７は、第１内輪および第２内輪の圧入代と、圧入後の第１内輪軌道および第２内輪軌道の傾斜角度と、第１内輪軌道の傾斜角度増大量との関係を示す線図である。FIG. 7 is a diagram showing the relationship between the press-fitting allowance of the first inner ring and the second inner ring, the inclination angle of the first inner ring raceway and the second inner ring raceway after press fitting, and the amount of increase in the inclination angle of the first inner ring raceway is there. 図８は、本発明の実施の形態の第２例を示す、第１内輪および第２内輪とハブ本体とを、互いに組み合わせる前の状態で示す断面図である。FIG. 8 is a cross-sectional view showing the first inner ring, the second inner ring, and the hub body before being combined with each other, showing a second example of the embodiment of the present invention. 図９は、従来の車輪支持用の複列円すいころ軸受ユニットの１例を示す断面図である。FIG. 9 is a sectional view showing an example of a conventional double-row tapered roller bearing unit for supporting a wheel.
　　［実施の形態の第１例］
　図１～図７は、本発明の実施の形態の第１例を示している。本例の特徴は、主に、ハブ２ａを組み立てた状態での第１内輪軌道７および第２内輪軌道８の傾斜角度を適正範囲に収めるために、各部分の寸法などを調整する点にある。本例の対象となる車輪支持用複列円すいころ軸受ユニットは、図９に示した従来構造と同様に、外輪１と、ハブ２ａと、複数個の円すいころ３とを備える。なお、図１は、本例の車輪支持用複列円すいころ軸受ユニットを、外輪１、複数個の円すいころ３、１対の保持器１７および１対の組み合わせシールリング１８など、一部の部品を省略した状態で示している。 [First example of embodiment]
1 to 7 show a first example of an embodiment of the present invention. The feature of this example is mainly to adjust the dimensions and the like of each part in order to keep the inclination angles of the first inner ring raceway 7 and the second inner ring raceway 8 in the assembled state in the hub 2a. . The double-row tapered roller bearing unit for wheel support, which is the object of this example, includes an outer ring 1, a hub 2a, and a plurality of tapered rollers 3, as in the conventional structure shown in FIG. FIG. 1 shows the wheel support double-row tapered roller bearing unit according to the present embodiment. The outer ring 1, a plurality of tapered rollers 3, a pair of cages 17 and a pair of combination seal rings 18 are part of the components. Is shown in a state where is omitted.
　外輪１は、内周面に形成された複列の外輪軌道４、５と、外周面に形成され、懸架装置のナックルに結合固定するための静止側フランジ６とを備える。複列の外輪軌道４、５のうち、軸方向内側に位置する第１外輪軌道４と、軸方向外側に位置する第２外輪軌道５とは、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面により構成される。 The outer ring 1 includes double row outer ring raceways 4 and 5 formed on the inner peripheral surface, and a stationary side flange 6 formed on the outer peripheral surface and coupled and fixed to the knuckle of the suspension device. Of the double-row outer ring raceways 4 and 5, the first outer ring raceway 4 positioned on the inner side in the axial direction and the second outer ring raceway 5 positioned on the outer side in the axial direction increase in diameter toward the direction away from each other in the axial direction. It is comprised by the partial conical surface inclined in the direction which becomes.
　ハブ２ａは、外輪１の内径側に、外輪１と同心に配置されている。ハブ２ａは、外周面の軸方向内端部および中間部にそれぞれに形成された、複列の内輪軌道７、８と、軸方向外端寄り部分で外輪１の内径側から軸方向に突出した部分に形成された、車輪を支持固定するための回転側フランジ９とを備える。複列の内輪軌道７、８のうち、軸方向内側に位置する第１内輪軌道７と、軸方向外側に位置する第２内輪軌道８とは、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面により構成される。 The hub 2a is disposed concentrically with the outer ring 1 on the inner diameter side of the outer ring 1. The hub 2a protrudes in the axial direction from the inner diameter side of the outer ring 1 at a portion closer to the outer end in the axial direction and the double-row inner ring raceways 7 and 8 formed respectively at the inner end and the intermediate portion of the outer peripheral surface. And a rotation-side flange 9 for supporting and fixing the wheel. Among the double-row inner ring raceways 7 and 8, the first inner ring raceway 7 located on the inner side in the axial direction and the second inner ring raceway 8 located on the outer side in the axial direction have larger diameters as they go away from each other in the axial direction. It is comprised by the partial conical surface inclined in the direction which becomes.
　ハブ２ａは、外周面に第１内輪軌道７を形成した円環状の第１内輪１０と、外周面に第２内輪軌道８を形成した円環状の第２内輪１１と、予圧調整に用いる円環状の間座２０と、回転側フランジ９を一体に形成したハブ本体１２ａとにより構成される。第１内輪軌道７（第２内輪軌道８）は、第１内輪１０（第２内輪１１）の外周面の小径側端部に設けられた小鍔部と大径側端部に設けられた大鍔部との間部分に設けられている。第２内輪１１は、ハブ本体１２ａの外周面の軸方向内端部から中間部に掛けて設けられた円筒状の嵌合面部１３ａの軸方向外半部に圧入することにより、締り嵌めで外嵌されている。第１内輪１０は、嵌合面部１３ａの軸方向内半部に圧入することにより、締り嵌めで外嵌されている。間座２０は、第１内輪１０の小径側端面と第２内輪１１の小径側端面との間に挟持されている。第１内輪１０の大径側端面は、ハブ本体１２ａの軸方向内端部に設けられた円筒部１４を径方向外方に塑性変形させることで形成されたかしめ部１５により抑え付けられている。したがって、第１内輪１０および第２内輪１１と、間座２０とは、嵌合面部１３ａの軸方向外端部に存在する段差面１６とかしめ部１５とにより軸方向両側から挟持され、ハブ本体１２ａに対し結合固定されている。 The hub 2a includes an annular first inner ring 10 having a first inner ring raceway 7 formed on an outer peripheral surface, an annular second inner ring 11 having a second inner ring raceway 8 formed on an outer peripheral surface, and an annular shape used for preload adjustment. A spacer 20 and a hub body 12a in which the rotation side flange 9 is integrally formed. The first inner ring raceway 7 (second inner ring raceway 8) is provided with a small flange portion provided at the small diameter end portion and a large diameter side end portion of the outer peripheral surface of the first inner ring 10 (second inner ring 11). It is provided in the part between the buttocks. The second inner ring 11 is externally fitted with an interference fit by press-fitting into the outer half in the axial direction of a cylindrical fitting surface portion 13a provided from the inner end in the axial direction of the outer peripheral surface of the hub body 12a to the intermediate portion. It is fitted. The first inner ring 10 is externally fitted with an interference fit by being press-fitted into the inner half of the fitting surface portion 13a in the axial direction. The spacer 20 is sandwiched between the small diameter side end surface of the first inner ring 10 and the small diameter side end surface of the second inner ring 11. The large-diameter side end face of the first inner ring 10 is held down by a caulking portion 15 formed by plastically deforming a cylindrical portion 14 provided at an axially inner end portion of the hub body 12a radially outward. . Accordingly, the first inner ring 10 and the second inner ring 11 and the spacer 20 are sandwiched from both sides in the axial direction by the step surface 16 and the caulking portion 15 existing at the outer end in the axial direction of the fitting surface portion 13a. It is fixedly coupled to 12a.
　円すいころ３は、第１外輪軌道４と第１内輪軌道７との間と、第２外輪軌道５と第２内輪軌道８との間とに、それぞれ複数個ずつ、保持器１７により保持された状態で転動自在に設けられている。外輪１の軸方向内端部内周面と第１内輪１０の大径側端部外周面との間、および、外輪１の軸方向外端部内周面と第２内輪１１の大径側端部外周面との間には、それぞれ組み合わせシールリング１８が組み付けられ、円すいころ３を設置した円筒状空間の軸方向両端開口が塞がれている。ハブ本体１２の径方向中心部には、駆動軸の先端部を挿入してスプライン係合させるためのスプライン孔１９が設けられている。 A plurality of tapered rollers 3 are held by a cage 17 between the first outer ring raceway 4 and the first inner ring raceway 7 and between the second outer ring raceway 5 and the second inner ring raceway 8, respectively. It is provided so that it can roll freely. Between the inner peripheral surface of the inner end portion in the axial direction of the outer ring 1 and the outer peripheral surface of the end portion on the large diameter side of the first inner ring 10 and the inner peripheral surface of the outer end portion in the axial direction of the outer ring 1 and the end portion on the large diameter side of the second inner ring 11. A combination seal ring 18 is assembled between each outer peripheral surface, and both axial ends of the cylindrical space in which the tapered rollers 3 are installed are closed. A spline hole 19 is provided at the center of the hub body 12 in the radial direction for inserting the tip of the drive shaft into spline engagement.
　図３（Ａ）～図３（Ｆ）は、本例の車輪支持用転がり軸受ユニットを構成するハブ２ａの組立方法を工程順に示している。ハブ２ａを組み立てるために、まず、図３（Ａ）に示した第２内輪１１を、図３（Ｂ）に示すように、ハブ本体１２ａの嵌合面部１３ａの軸方向外端部に、軸方向内側から圧入により外嵌する。次に、図３（Ｃ）に示すように、嵌合面部１３ａのうち、第２内輪１１の軸方向内側に隣接する部分である軸方向中間部に設けられた段部２１の周囲に、間座２０を隙間嵌めで外嵌する。次いで、図３（Ｄ）に示した第１内輪１０を、図３（Ｅ）に示すように、嵌合面部１３ａのうち、間座２０の軸方向内側に隣接する部分である軸方向内端寄り部分に、軸方向内側から圧入することにより、締り嵌めで外嵌する。そして、図３（Ｆ）に示すように、ハブ本体１２ａの軸方向内端部に設けられた円筒部１４のうち、第１内輪１０よりも軸方向内側に突出した部分を外径側に塑性変形させることで、かしめ部１５を形成して、かしめ部１５により第１内輪１０の大径側端面（軸方向内端面）を抑え付ける。 3 (A) to 3 (F) show an assembling method of the hub 2a constituting the wheel bearing rolling bearing unit of this example in the order of steps. In order to assemble the hub 2a, first, the second inner ring 11 shown in FIG. 3A is connected to the axially outer end of the fitting surface portion 13a of the hub body 12a as shown in FIG. It fits by press-fitting from the inner side. Next, as shown in FIG. 3 (C), around the stepped portion 21 provided in the intermediate portion in the axial direction which is a portion adjacent to the inner side in the axial direction of the second inner ring 11 in the fitting surface portion 13a. The seat 20 is externally fitted with a gap fit. Next, as shown in FIG. 3 (E), the first inner ring 10 shown in FIG. 3 (D) is an axial inner end that is a portion adjacent to the inner side in the axial direction of the spacer 20 in the fitting surface portion 13a. By press-fitting into the side portion from the inner side in the axial direction, the outer portion is fitted with an interference fit. As shown in FIG. 3 (F), a portion of the cylindrical portion 14 provided at the axially inner end portion of the hub body 12a that protrudes inward in the axial direction from the first inner ring 10 is plasticized toward the outer diameter side. By deforming, the caulking portion 15 is formed, and the caulking portion 15 suppresses the large-diameter side end surface (the axial inner end surface) of the first inner ring 10.
　本例の車輪支持用複列円すいころ軸受ユニットについては、次の前提事項１および２が成立する。 For the double-row tapered roller bearing unit for wheel support in this example, the following assumptions 1 and 2 hold.
　＜前提事項１＞
　嵌合面部１３ａに第１内輪１０および第２内輪１１を圧入により外嵌することにより、第１内輪１０および第２内輪１１が拡径方向に弾性変形する。具体的には、小径側の肉が大径側の肉よりも薄いため、小径側が大径側よりも比較的大きく拡径する態様で弾性変形する。このような弾性変形に伴い、第１内輪軌道７および第２内輪軌道８の傾斜角度が減少する。すなわち、嵌合面部１３ａに第１内輪１０を圧入により外嵌する前の状態（自由状態）での第１内輪軌道７の傾斜角度θ1と、嵌合面部１３ａに第１内輪１０を圧入により外嵌した後の第１内輪軌道７の傾斜角度Θ1との関係は、図４（Ｂ）の左半部に示すように、θ1＞Θ1となる。また、嵌合面部１３ａに第２内輪１１を圧入により外嵌する前の状態（自由状態）での第２内輪軌道８の傾斜角度θ2と、嵌合面部１３ａに第２内輪１１を圧入により外嵌した後の第２内輪軌道８の傾斜角度Θ2との関係は、図４（Ａ）に示すように、θ2＞Θ2となる。なお、嵌合面部１３ａに第１内輪１０（または第２内輪１１）を圧入により外嵌することに伴って生じる第１内輪軌道７（または第２内輪軌道８）の傾斜角度減少量（絶対値）δθa＝θ1－Θ1（またはδθb＝θ2－Θ2）と、嵌合面部１３ａに対する第１内輪１０（または第２内輪１１）の圧入代ΔＸ1（またはΔＸ2）との関係は、実験や弾性ＦＥＭ解析によって具体的に求められ、図５に示すように、ほぼ直線（比例関係）になる。 <Assumption 1>
By fitting the first inner ring 10 and the second inner ring 11 to the fitting surface portion 13a by press fitting, the first inner ring 10 and the second inner ring 11 are elastically deformed in the diameter increasing direction. Specifically, since the meat on the small diameter side is thinner than the meat on the large diameter side, the small diameter side is elastically deformed in such a manner that the diameter is relatively larger than that on the large diameter side. With such elastic deformation, the inclination angles of the first inner ring raceway 7 and the second inner ring raceway 8 decrease. That is, the inclination angle θ 1 of the first inner ring raceway 7 in a state (free state) before the first inner ring 10 is fitted onto the fitting surface portion 13a by press fitting, and the first inner ring 10 is pressed into the fitting surface portion 13a. The relationship with the inclination angle Θ 1 of the first inner ring raceway 7 after the outer fitting is θ 1 > Θ 1 as shown in the left half of FIG. Further, the inclination angle θ 2 of the second inner ring raceway 8 in a state (free state) before the second inner ring 11 is press-fitted into the fitting surface portion 13a, and the second inner ring 11 is pressed into the fitting surface portion 13a. The relationship with the inclination angle Θ 2 of the second inner ring raceway 8 after the outer fitting is θ 2 > Θ 2 as shown in FIG. The amount of decrease in the inclination angle (absolute value) of the first inner ring raceway 7 (or the second inner ring raceway 8) that is generated when the first inner ring 10 (or the second inner ring 11) is fitted onto the fitting surface portion 13a by press fitting. ) Δθ a = θ 1 −Θ 1 (or δθ b = θ 2 −Θ 2 ) and the press-fit allowance ΔX 1 (or ΔX 2 ) of the first inner ring 10 (or the second inner ring 11) with respect to the fitting surface portion 13a. The relationship is specifically obtained by experiment or elastic FEM analysis, and is almost a straight line (proportional relationship) as shown in FIG.
＜前提事項２＞
　かしめ部１５を形成することにより、第１内輪１０のうちの大径側端部が拡径方向に弾性変形することに伴い、第１内輪軌道７の傾斜角度が増大する。すなわち、かしめ部１５を形成する前の状態での第１内輪軌道７の傾斜角度Θ1と、かしめ部１５を形成した後の第１内輪軌道７の傾斜角度φ1との関係は、図４（Ｂ）の右半部に示すように、Θ1＜φ1となる。なお、前提事項２に関して、かしめ部１５を形成することに伴って生じる第１内輪軌道７の傾斜角度増大量（絶対値）δθk（＝φ1－Θ1）は、実験や弾塑性ＦＥＭ解析によって具体的に求めることができる。 <Assumption 2>
By forming the caulking portion 15, the inclination angle of the first inner ring raceway 7 increases as the large diameter side end portion of the first inner ring 10 is elastically deformed in the diameter increasing direction. That is, the relationship between the inclination angle Θ 1 of the first inner ring raceway 7 before the caulking portion 15 is formed and the inclination angle φ 1 of the first inner ring raceway 7 after the caulking portion 15 is formed is shown in FIG. As shown in the right half of (B), Θ 1 <φ 1 . Note that with respect to the premise 2, the amount of increase in the inclination angle (absolute value) δθ k (= φ 1 −Θ 1 ) of the first inner ring raceway 7 that accompanies the formation of the caulking portion 15 is determined by experiment or elasto-plastic FEM analysis. Can be specifically obtained.
　本例の場合、前提事項１および２を考慮して、ハブ２ａを組み立てた状態、すなわち、かしめ部１５を形成した状態での、第１内輪軌道７の傾斜角度φ1と、第２内輪軌道８の傾斜角度Θ2とを、互いに同一の適正範囲内に収める（高精度でφ1＝Θ2とする）ようにしている。 In the case of this example, in consideration of the assumptions 1 and 2, the inclination angle φ 1 of the first inner ring raceway 7 and the second inner ring raceway in the state where the hub 2a is assembled, that is, in the state where the caulking portion 15 is formed. The inclination angle Θ 2 of 8 is set within the same appropriate range (with high accuracy φ 1 = Θ 2 ).
　まず、前提事項１より、次の（１）式および（２）式が成立する。なお、嵌合面部１３ａに対する第１内輪１０（または第２内輪１１）の圧入代がΔＸ1（またはΔＸ2）である場合の第１内輪軌道７（または第２内輪軌道８）の傾斜角度減少量δθa（またはδθb）を、δθa（ΔＸ1）（またはδθb（ΔＸ2））と表記する。
　　Θ1　＝　θ1－δθa（ΔＸ1）　　・・・（１）
　　Θ2　＝　θ2－δθb（ΔＸ2）　　・・・（２） First, from the assumption 1, the following expressions (1) and (2) are established. Note that the inclination angle of the first inner ring raceway 7 (or second inner ring raceway 8) is reduced when the press-fit allowance of the first inner ring 10 (or second inner ring 11) to the fitting surface portion 13a is ΔX 1 (or ΔX 2 ). The quantity δθ a (or δθ b ) is expressed as δθ a (ΔX 1 ) (or δθ b (ΔX 2 )).
Θ 1 = θ 1 −δθ a (ΔX 1 ) (1)
Θ 2 = θ 2 −δθ b (ΔX 2 ) (2)
　次に、上述した前提事項２より、次の（３）式が成立する。
　　φ1　＝　Θ1＋δθk　＝　θ1－δθa（ΔＸ1）＋δθk　　・・・（３） Next, the following formula (3) is established from the above-mentioned premise 2.
φ 1 = Θ 1 + δθ k = θ 1 −δθ a (ΔX 1 ) + δθ k (3)
　なお、かしめ部１５の形成に際して、第２内輪軌道８の傾斜角度Θ2は変化しない。 Note that when the caulking portion 15 is formed, the inclination angle Θ 2 of the second inner ring raceway 8 does not change.
　ハブ２ａを組み立てた状態での、第１内輪軌道７の傾斜角度φ1と、第２内輪軌道８の傾斜角度Θ2とを、互いに同一の適正範囲内に収める（高精度でφ1＝Θ2とする）ためには、（２）式＝（３）式となるように、すなわち、次の（４）式の関係を満たすようにすればよい。
　　－θ1＋δθa（ΔＸ1）＋θ2－δθb（ΔＸ2）　＝　δθk　　・・・（４） The inclination angle φ 1 of the first inner ring raceway 7 and the inclination angle Θ 2 of the second inner ring raceway 8 in the assembled state of the hub 2a are within the same appropriate range (φ 1 = Θ with high accuracy) 2 to) because, as a (2) = (3), i.e., it suffices to satisfy the following equation (4) relationship.
−θ 1 + δθ a (ΔX 1 ) + θ 2 −δθ b (ΔX 2 ) = δθ k (4)
　特に、θ1＝θ2とする場合には、次の（５）式の関係を満たすようにする。
　　δθa（ΔＸ1）－δθb（ΔＸ2）　＝　δθk　　・・・（５） In particular, when θ 1 = θ 2 , the relationship of the following equation (5) is satisfied.
δθ a (ΔX 1 ) −δθ b (ΔX 2 ) = δθ k (5)
　圧入代ΔＸ1、ΔＸ2には、それぞれ上限値および下限値を設定する必要がある。すなわち、圧入代ΔＸ1、ΔＸ2を大きくし過ぎると、嵌合面部１３ａに第１内輪１０および第２内輪１１を圧入することで、第１内輪１０および第２内輪１１に作用するフープ応力（円周方向応力）が過大になる。この結果、第１内輪１０および第２内輪１１に割れが生じやすくなったり、第１内輪軌道７および第２内輪軌道８の寿命低下を招きやすくなったりする。そこで、これらの不都合が発生しないようにするために、圧入代ΔＸ1、ΔＸ2には、それぞれ上限値ΔＭを設定する必要がある。一方、圧入代ΔＸ1、ΔＸ2を小さくし過ぎると、嵌合面部１３ａと第１内輪１０または第２内輪１１との嵌合部にクリープが生じやすくなる。したがって、このような不都合が発生しないようにするために、圧入代ΔＸ1、ΔＸ2には、それぞれ下限値Δｍを設定する必要がある。つまり、圧入代ΔＸ1、ΔＸ2は、次の（６）式の範囲内に収める必要がある。
　　Δｍ≦（ΔＸ1、ΔＸ2）≦ΔＭ　　・・・（６） It is necessary to set an upper limit value and a lower limit value for the press-fit allowances ΔX 1 and ΔX 2 , respectively. That is, if the press-fitting allowances ΔX 1 and ΔX 2 are excessively increased, the first inner ring 10 and the second inner ring 11 are press-fitted into the fitting surface portion 13 a, so that the hoop stress acting on the first inner ring 10 and the second inner ring 11 ( Circumferential stress) becomes excessive. As a result, the first inner ring 10 and the second inner ring 11 are likely to be cracked, and the life of the first inner ring raceway 7 and the second inner ring raceway 8 is likely to be reduced. Therefore, in order to prevent these inconveniences, it is necessary to set an upper limit value ΔM for each of the press-fitting allowances ΔX 1 and ΔX 2 . On the other hand, if the press-fitting allowances ΔX 1 and ΔX 2 are too small, creep tends to occur at the fitting portion between the fitting surface portion 13 a and the first inner ring 10 or the second inner ring 11. Therefore, in order to prevent such inconvenience, it is necessary to set a lower limit value Δm for each of the press-fit allowances ΔX 1 and ΔX 2 . That is, the press-fit allowances ΔX 1 and ΔX 2 need to be within the range of the following equation (6).
Δm ≦ (ΔX 1 , ΔX 2 ) ≦ ΔM (6)
　以上の説明をまとめると、図６および図７に示すように、（６）式の範囲内で、（５）式（θ1＝θ2とする場合）または（４）式（θ1≠θ2とする場合）の関係を満足するような設計を行えば、上述のような不都合を生じることなく、ハブ２ａを組み立てた状態での、第１内輪軌道７の傾斜角度φ1と、第２内輪軌道８の傾斜角度Θ2とを、互いに同一の適正範囲内に収める（高精度でφ1＝Θ2とする）ことができる。 To summarize the above description, as shown in FIGS. 6 and 7, within the range of the equation (6), the equation (5) (when θ 1 = θ 2 ) or the equation (4) (θ 1 ≠ θ 2 ), the inclination angle φ 1 of the first inner ring raceway 7 in the assembled state of the hub 2a without causing the inconvenience as described above, and the second The inclination angle Θ 2 of the inner ring raceway 8 can be within the same appropriate range (with high accuracy φ 1 = Θ 2 ).
　そこで、本例の場合には、第１内輪１０および第２内輪１１として、材質、嵌合面部１３ａに第１内輪１０および第２内輪１１を圧入により外嵌する前の状態（自由状態）での形状および寸法などの諸元が、製造上不可避な誤差を除いて実質的に等しいものを使用している。つまり、嵌合面部１３ａに第１内輪１０および第２内輪１１を圧入により外嵌する前の状態での、第１内輪１０の内径寸法ｄ１と、第２内輪１１の内径寸法ｄ2を実質的に等しく（ｄ1＝ｄ2と）し、かつ、第１内輪軌道７の傾斜角度θ１と、第２内輪軌道８の傾斜角度θ2を実質的に等しく（θ1＝θ2と）している。 Therefore, in the case of the present example, the first inner ring 10 and the second inner ring 11 are made of a material and in a state (free state) before the first inner ring 10 and the second inner ring 11 are fitted onto the fitting surface portion 13a by press fitting. The specifications such as the shape and dimensions are substantially the same except for inevitable manufacturing errors. That is, in a state before fitted by press-fitting the first inner ring 10 and second inner ring 11 to the fitting surface 13a, the inner diameter d 1 of the first inner ring 10, an inner diameter d 2 of the second inner ring 11 substantially to equal (d 1 = d 2 and) and, and the inclination angle theta 1 of the first inner ring raceway 7, the inclination angle theta 2 of the second inner ring raceway 8 (and theta 1 = theta 2) substantially equal is doing.
　また、（５）式の関係を満足させるために、嵌合面部１３ａのうち、第１内輪１０を外嵌する部分と第２内輪１１を外嵌する部分との間の位置であり、間座２０が内径側に位置する部分に、部分円すい面（テーパ面）状の段部２１を設けている。これにより、嵌合面部１３ａのうち、第１内輪１０を外嵌する軸方向内側部分を、第１内輪１０を圧入により外嵌する前の状態での外径寸法がＤ1である大径部２２とし、第２内輪１１を外嵌する軸方向外側部分を、第２内輪１１を圧入により外嵌する前の状態での外径寸法がＤ2（＜Ｄ1）である小径部２３としている。そして、大径部２２と小径部２３との間に径差（Ｄ2＜Ｄ1）を設けることに基づいて、第１内輪１０の圧入代ΔＸ1＝Ｄ1－ｄ1を、第２内輪１０の圧入代ΔＸ2＝Ｄ2－ｄ2よりも、（６）式の範囲内で大きく（ΔＸ1＞ΔＸ2と）している。これにより、傾斜角度減少量δθa（ΔＸ1）を傾斜角度減少量δθb（ΔＸ2）よりも大きく（δθa（ΔＸ1）＞δθb（ΔＸ2）と）すると共に、傾斜角度減少量δθa（ΔＸ1）、δθb（ΔＸ2）同士の差δθa（ΔＸ1）－δθb（ΔＸ2）と、傾斜角度増大量δθkとを、実質的に等しくすることで、（５）式の関係を満足させるようにしている。 Moreover, in order to satisfy the relationship of Formula (5), it is a position between the part which externally fits the 1st inner ring | wheel 10 and the part which externally fits the 2nd inner ring | wheel 11 among the fitting surface parts 13a, and a spacer A step portion 21 having a partially conical surface (tapered surface) shape is provided in a portion where 20 is located on the inner diameter side. Thus, among the engagement surface portion 13a, the axial inner portion fitted around the first inner ring 10, the large diameter portion outside diameter in the state before fitted by press-fitting the first inner ring 10 is by D 1 22, the axially outer portion where the second inner ring 11 is externally fitted is a small diameter portion 23 whose outer diameter dimension is D 2 (<D 1 ) before the second inner ring 11 is externally fitted by press-fitting. . Then, based on providing a diameter difference (D 2 <D 1 ) between the large-diameter portion 22 and the small-diameter portion 23, the press-fit allowance ΔX 1 = D 1 -d 1 of the first inner ring 10 is changed to the second inner ring. It is larger than the press-fitting allowance ΔX 2 = D 2 −d 2 of 10 within the range of the expression (6) (ΔX 1 > ΔX 2 ). As a result, the tilt angle decrease amount δθ a (ΔX 1 ) is made larger than the tilt angle decrease amount δθ b (ΔX 2 ) (δθ a (ΔX 1 )> δθ b (ΔX 2 )), and the tilt angle decrease amount is increased. δθ a (ΔX 1), δθ b (ΔX 2) the difference between δθ a (ΔX 1) -δθ b and ([Delta] X 2), and a tilt angle increase amount .delta..theta k, by substantially equal, (5 ) Is satisfied.
　上述のように、本例の複列円すいころ軸受ユニットおよびその製造方法の場合には、かしめ部１５の形成に伴う第１内輪軌道７の傾斜角度増大量δθkだけでなく、嵌合面部１３ａに第１内輪１０および第２内輪１１を圧入により外嵌することに伴う第１内輪軌道７の傾斜角度減少量δθa（ΔＸ1）および第２内輪軌道８の傾斜角度減少量δθb（ΔＸ2）をも考慮して、かしめ部１５を形成した後の状態での第１内輪軌道７の傾斜角度φ1と第２内輪軌道８の傾斜角度Θ2との調整を行う。このため、これらの傾斜角度φ1、Θ2を、互いに同一の適正範囲の中央値（最も理想的な値）に十分に近づける（高精度でφ1＝Θ2とする）ことができる。この結果、第１内輪軌道７および第２内輪軌道８、並びに、第１外輪軌道４および第２外輪軌道５と複数個の円すいころ３のそれぞれの転動面との当接状態を向上させることができる。したがって、車輪支持用複列円すいころ軸受ユニットの耐久性をより向上させることができる。 As described above, in the case of the double-row tapered roller bearing unit and the manufacturing method thereof of this example, not only the inclination angle increase amount δθ k of the first inner ring raceway 7 associated with the formation of the caulking portion 15 but also the fitting surface portion 13a. tilt angle reduction .delta..theta b ([Delta] X of the first inclined angle reduction δθ a (ΔX 1) of the first inner ring raceway 7 due to be fitted by press-fitting the inner ring 10 and second inner ring 11 and the second inner ring raceway 8 2 ) is also considered, and the inclination angle φ 1 of the first inner ring raceway 7 and the inclination angle Θ 2 of the second inner ring raceway 8 in the state after the caulking portion 15 is formed are adjusted. Therefore, these inclination angles φ 1 and Θ 2 can be made sufficiently close to the median value (the most ideal value) within the same appropriate range (with high accuracy φ 1 = Θ 2 ). As a result, the contact state between the first inner ring raceway 7 and the second inner ring raceway 8, and the first outer ring raceway 4 and the second outer ring raceway 5, and the respective rolling surfaces of the tapered rollers 3 is improved. Can do. Therefore, the durability of the double-row tapered roller bearing unit for wheel support can be further improved.
　また、本例の場合には、第１内輪１０および第２内輪１１として、材質、形状、寸法などの諸元が実質的に等しいものを使用する。このため、第１内輪軌道７および第２内輪軌道８に仕上げの研削加工を施す装置を共通化できるなどに基づいて、品質および生産性の確保と低コスト化とを図りやすい。また、第１内輪１０の小径側端面と第２内輪１１の小径側端面との間に間座２０を挟持すると共に、嵌合面部１３ａのうち、間座２０の内径側に位置する部分に、段部２１を設けている。このため、段部２１に第１内輪１０または第２内輪１１が外嵌された状態になることを防止して、圧入代ΔＸ1またはΔＸ2にばらつきが生じるなどの悪影響が及ぶことを防止できる。 In the case of this example, the first inner ring 10 and the second inner ring 11 are substantially the same in terms of material, shape, dimensions, and the like. For this reason, it is easy to ensure quality and productivity and reduce costs based on the fact that a device for finishing grinding can be used in common for the first inner ring raceway 7 and the second inner ring raceway 8. Further, the spacer 20 is sandwiched between the small-diameter side end surface of the first inner ring 10 and the small-diameter side end surface of the second inner ring 11, and the portion of the fitting surface portion 13a located on the inner diameter side of the spacer 20 is A stepped portion 21 is provided. For this reason, it is possible to prevent the first inner ring 10 or the second inner ring 11 from being externally fitted to the step portion 21 and to prevent adverse effects such as variations in the press-fitting allowance ΔX 1 or ΔX 2. .
　本発明は、従動輪用の車輪支持用複列円すいころ軸受ユニットや車輪支持用以外の複列円すいころ軸受ユニットに適用することもできる。また、本発明は、使用状態で外径側軌道輪部材が回転し、内径側軌道輪部材が回転しない複列円すいころ軸受ユニットに適用することもできる。 The present invention can also be applied to a double-row tapered roller bearing unit for supporting a wheel for a driven wheel or a double-row tapered roller bearing unit other than for supporting a wheel. The present invention can also be applied to a double-row tapered roller bearing unit in which the outer diameter side race ring member rotates in use and the inner diameter side race ring member does not rotate.
　また、本発明を実施する場合には、第１内輪の小径側端面と、第２内輪の小径側端面との間に、必ずしも間座を挟持する必要はない。また、本発明を実施する場合には、軸部材に第１内輪および第２内輪を圧入により外嵌する前の状態（自由状態）での第１内輪軌道の傾斜角度θ１と、第２内輪軌道の傾斜角度θ2とを互いに異ならせることもできるし、かしめ部を形成した後の状態での、第１内輪軌道の傾斜角度φ1の適正範囲と第２内輪軌道の傾斜角度Θ2の適正範囲とを互いに異ならせることもできる。 Moreover, when implementing this invention, it is not necessary to pinch a spacer between the small diameter side end surface of the first inner ring and the small diameter side end surface of the second inner ring. When the present invention is carried out, the inclination angle θ 1 of the first inner ring raceway in the state (free state) before the first inner ring and the second inner ring are fitted onto the shaft member by press fitting, and the second inner ring The inclination angle θ 2 of the track can be made different from each other, and the appropriate range of the inclination angle φ 1 of the first inner ring track and the inclination angle Θ 2 of the second inner ring track in the state after the caulking portion is formed. The appropriate range can be different from each other.
　　［実施の形態の第２例］
　図８は、本発明の実施の形態の第２例を示している。本例の場合、ハブ本体１２ｂを構成する回転側フランジ９の付け根部分の強度を向上させるために、回転側フランジ９の内側面の径方向内端部（段差面１６）と嵌合面部１３との連続部に存在する隅Ｒ部２４ａの曲率半径を、実施の形態の第１例に係るハブ本体１２ａの隅Ｒ部２４の曲率半径よりも大きくしている。これに伴い、隅Ｒ部２４ａと対向する位置に配置される、第２内輪１１ａの内周面と大径側端面との連続部に存在するＲ面取り部２６ａの曲率半径も、実施の形態の第１例における第２内輪１１のＲ面取り部２６の曲率半径よりも大きくしている。これにより、Ｒ面取り部２６ａが隅Ｒ部２４ａと干渉して、第２内輪１１ａの大径側端面が段差面１６に当接しなくなることを防止している。したがって、本例の場合、第２内輪１１ａのＲ面取り部２６ａの曲率半径は、第１内輪１０の内周面と大径側端面との連続部に存在するＲ面取り部２５の曲率半径よりも大きくなっている。つまり、少なくともこの点で、第１内輪１０の諸元と第２内輪１１ａの諸元とは互いに異なっている。 [Second Example of Embodiment]
FIG. 8 shows a second example of the embodiment of the present invention. In the case of this example, in order to improve the strength of the base portion of the rotation side flange 9 constituting the hub body 12b, the radially inner end portion (step surface 16) of the inner side surface of the rotation side flange 9 and the fitting surface portion 13 The radius of curvature of the corner R portion 24a existing in the continuous portion is larger than the radius of curvature of the corner R portion 24 of the hub body 12a according to the first example of the embodiment. Accordingly, the radius of curvature of the R chamfered portion 26a that is located at the continuous portion between the inner peripheral surface of the second inner ring 11a and the large-diameter side end surface that is disposed at a position facing the corner R portion 24a is also the same as that of the embodiment. It is larger than the radius of curvature of the R chamfered portion 26 of the second inner ring 11 in the first example. This prevents the R chamfered portion 26 a from interfering with the corner R portion 24 a and preventing the large-diameter side end surface of the second inner ring 11 a from coming into contact with the stepped surface 16. Therefore, in the case of this example, the radius of curvature of the R chamfered portion 26a of the second inner ring 11a is larger than the radius of curvature of the R chamfered portion 25 existing at the continuous portion between the inner peripheral surface of the first inner ring 10 and the large diameter side end surface. It is getting bigger. That is, at least in this respect, the specifications of the first inner ring 10 and the specifications of the second inner ring 11a are different from each other.
　また、本例の場合には、（５）式の関係を満足させるために、嵌合面部１３のうち、第１内輪１０を外嵌する部分と第２内輪１１ａを外嵌する部分とを互いに連続した単一円筒面（自由状態での外径寸法Ｄ）とし、かつ、第１内輪１０の嵌合面部１３に圧入することにより、締り嵌めで外嵌する前の状態での内径寸法ｄ1を、第２内輪１１ａの嵌合面部１３に圧入することにより、締り嵌めで外嵌する前の状態での内径寸法ｄ2よりも小さく（ｄ1＜ｄ2と）することに基づいて、第１内輪１０の圧入代ΔＸ1＝Ｄ－ｄ1を、第２内輪１１ａの圧入代ΔＸ2＝Ｄ－ｄ2よりも、（６）式の範囲内で大きく（ΔＸ1＞ΔＸ2と）している。これにより、第１内輪軌道７の傾斜角度減少量δθa（ΔＸ1）を第２内輪軌道８の傾斜角度減少量δθb（ΔＸ2）よりも大きく（δθa（ΔＸ1）＞δθb（ΔＸ2）と）すると共に、これらの傾斜角度減少量δθa（ΔＸ1）、δθb（ΔＸ2）同士の差δθa（ΔＸ1）－δθb（ΔＸ2）と、傾斜角度増大量δθkとを、実質的に等しくすることで、（５）式の関係を満足させるようにしている。 Further, in the case of this example, in order to satisfy the relationship of the expression (5), the portion of the fitting surface portion 13 that externally fits the first inner ring 10 and the portion that externally fits the second inner ring 11a are mutually connected. By adopting a continuous single cylindrical surface (outer diameter dimension D in a free state) and press-fitting into the fitting surface portion 13 of the first inner ring 10, the inner diameter dimension d 1 in the state before the outer fitting by the interference fit. and by press-fitting to the fitting surface 13 of the second inner ring 11a, smaller than the inner diameter d 2 of the previous state fitted with interference fit (and d 1 <d 2) based on the, the the press-fit allowance [Delta] X 1 = D-d 1 of 1 the inner ring 10, than press-fitting margin [Delta] X 2 = D-d 2 of the second inner ring 11a, and (6) increased within formula (a [Delta] X 1> [Delta] X 2) ing. As a result, the inclination angle reduction amount δθ a (ΔX 1 ) of the first inner ring raceway 7 is larger than the inclination angle reduction amount δθ b (ΔX 2 ) of the second inner ring raceway 8 (δθ a (ΔX 1 )> δθ b ( with [Delta] X 2) and), these inclination angles decrease δθ a (ΔX 1), δθ b (ΔX 2) the difference between δθ a (ΔX 1) and -δθ b (ΔX 2), the inclination angle increases the amount .delta..theta By making k substantially equal, the relationship of equation (5) is satisfied.
　本例の複列円すいころ軸受ユニットおよびその製造方法の場合には、嵌合面部１３を単一円筒面としており、嵌合面部１３の軸方向中間部に応力集中源となる段部を設けていないため、実施の形態の第１例の場合に比べて、ハブ本体１２ｂの強度を確保する設計を行いやすく、ハブ本体１２ｂの生産性の確保と低コスト化とを図りやすい。その他の構成および作用は、実施の形態の第１例と同様である。 In the case of the double-row tapered roller bearing unit of this example and the manufacturing method thereof, the fitting surface portion 13 is a single cylindrical surface, and a step portion serving as a stress concentration source is provided at the axial intermediate portion of the fitting surface portion 13. Therefore, as compared with the case of the first example of the embodiment, it is easy to design to ensure the strength of the hub main body 12b, and it is easy to ensure the productivity of the hub main body 12b and reduce the cost. Other configurations and operations are the same as those of the first example of the embodiment.
　なお、本例の場合、第２内輪１１ａのＲ面取り部２６ａを、Ｃ面取り部に変更することもできる。この場合、Ｃ面取り部の軸方向幅寸法および径方向幅寸法を、第１内輪１０のＲ面取り部２５の曲率半径（実施の形態の第１例の第２内輪１１のＲ面取り部２６の曲率半径）よりも大きくすれば、その分、回転側フランジ９の付け根部分に存在する隅Ｒ部２４ａの曲率半径を大きくでき、この付け根部分の強度を向上させることができる。 In the case of this example, the R chamfered portion 26a of the second inner ring 11a can be changed to a C chamfered portion. In this case, the axial width dimension and the radial width dimension of the C chamfered portion are set to the curvature radius of the R chamfered portion 25 of the first inner ring 10 (the curvature of the R chamfered portion 26 of the second inner ring 11 of the first example of the embodiment). The radius of curvature of the corner R portion 24a existing at the base portion of the rotation side flange 9 can be increased correspondingly, and the strength of the base portion can be improved.
　１　外輪
　２、２ａ　ハブ
　３　円すいころ
　４　第１外輪軌道
　５　第２外輪軌道
　６　静止側フランジ
　７　第１内輪軌道
　８　第２内輪軌道
　９　回転側フランジ
　１０　第１内輪
　１１、１１ａ　第２内輪
　１２、１２ａ、１２ｂ　ハブ本体
　１３、１３ａ　嵌合面部
　１４　円筒部
　１５　かしめ部
　１６　段差面
　１７　保持器
　１８　組み合せシールリング
　１９　スプライン孔
　２０　間座
　２１　段部
　２２　大径部
　２３　小径部
　２４、２４ａ　隅Ｒ部
　２５　Ｒ面取り部　
　２６、２６ａ　Ｒ面取り部 1 outer ring 2, 2a hub 3 tapered roller 4 first outer ring raceway 5 second outer ring raceway 6 stationary side flange 7 first inner ring raceway 8 second inner ring raceway 9 rotation side flange 10 first inner race 11, 11a second inner race 12, 12a , 12b Hub body 13, 13a Fitting surface portion 14 Cylindrical portion 15 Caulking portion 16 Step surface 17 Cage 18 Combination seal ring 19 Spline hole 20 Spacer 21 Step portion 22 Large diameter portion 23 Small diameter portion 24, 24a Corner R portion 25 R Chamfer
26, 26a R chamfer

Claims (14)

  1. 　内周面に、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面によりそれぞれ構成された、第１外輪軌道および第２外輪軌道を有する外径側軌道輪部材と、
    　外周面に、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面によりそれぞれ構成された、第１内輪軌道および第２外輪軌道を有する内径側軌道輪部材と、
    　第１外輪軌道と第１内輪軌道との間、および、第２外輪軌道と第２内輪軌道との間に、それぞれ複数個ずつ転動自在に設けられた円すいころと、
    を備え、
    　前記内径側軌道輪部材は、外周面に第１内輪軌道が形成された第１内輪と、外周面に第２内輪軌道が形成された第２内輪と、軸部材とを備え、第１内輪および第２内輪が、前記軸部材に圧入により外嵌され、かつ、該軸部材の軸方向片端部に塑性変形により形成されたかしめ部により、第１内輪の大径側端面を抑え付けることで、第１内輪および第２内輪が前記軸部材に結合固定されることにより構成され、
    　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪軌道の傾斜角度θ1と、
    　前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪軌道の傾斜角度θ2と、
    　前記軸部材に第１内輪を圧入により外嵌することに伴って生じる第１内輪軌道の傾斜角度減少量δθaと、
    　前記軸部材に第２内輪を圧入により外嵌することに伴って生じる第２内輪軌道の傾斜角度減少量δθbと、
    　前記かしめ部を形成することに伴って生じる第１内輪軌道の傾斜角度増大量δθkと、
    　前記軸部材に対する第１内輪の圧入代ΔＸ1と、
    　前記軸部材に対する第２内輪の圧入代ΔＸ2と、
    の関係が、次式：
    　－θ1＋δθa（ΔＸ1）＋θ2－δθb（ΔＸ2）＝δθk　
    を満たし、
    　前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ1と第２内輪軌道の傾斜角度Θ2とが、それぞれの適正範囲内に収められていることを特徴とする、複列円すいころ軸受ユニット。     An outer-diameter-side track ring member having a first outer ring raceway and a second outer ring raceway, each of which is constituted by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the inner peripheral surface;
    An inner diameter side race ring member having a first inner ring raceway and a second outer ring raceway, each formed by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the outer peripheral surface;
    A plurality of tapered rollers each provided between the first outer ring raceway and the first inner ring raceway and between the second outer ring raceway and the second inner ring raceway;
    With
    The inner diameter side race ring member includes a first inner ring having a first inner ring raceway formed on an outer peripheral surface, a second inner ring having a second inner ring raceway formed on an outer peripheral surface, and a shaft member. The second inner ring is externally fitted to the shaft member by press fitting, and the large-diameter side end surface of the first inner ring is suppressed by a caulking portion formed by plastic deformation at one axial end portion of the shaft member. The first inner ring and the second inner ring are configured by being coupled and fixed to the shaft member,
    An inclination angle θ 1 of the first inner ring raceway in a state before the first inner ring is fitted onto the shaft member by press fitting;
    An inclination angle θ 2 of the second inner ring raceway in a state before the second inner ring is fitted over the shaft member by press fitting;
    A tilt angle reduction amount δθ a of the first inner ring raceway that is generated when the first inner ring is fitted onto the shaft member by press fitting;
    A tilt angle reduction amount δθ b of the second inner ring raceway that is generated when the second inner ring is fitted on the shaft member by press fitting;
    A tilt angle increase amount δθ k of the first inner ring raceway that is generated when the caulking portion is formed, and
    A pressure allowance ΔX 1 of the first inner ring with respect to the shaft member;
    A press-fitting allowance ΔX 2 of the second inner ring with respect to the shaft member;
    The relationship is:
    −θ 1 + δθ a (ΔX 1 ) + θ 2 −δθ b (ΔX 2 ) = δθ k
    The filling,
    The inclination angle φ 1 of the first inner ring raceway and the inclination angle Θ 2 of the second inner ring race in the state after the caulking portion is formed are within the respective appropriate ranges. Row tapered roller bearing unit.
  2. 　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法と、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法とが実質的に等しく、
    　前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分との間に段部が設けられ、前記軸部材の外周面のうちの第１内輪が外嵌される部分の、該軸部材に第１内輪を圧入により外嵌する前の状態での外径寸法が、前記軸部材の外周面のうちの第２内輪が外嵌される部分の、該軸部材に第２内輪を圧入により外嵌する前の状態での外径寸法よりも大きい、
    請求項１に記載の複列円すいころ軸受ユニット。     The inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting. Is substantially equal to
    Of the outer peripheral surface of the shaft member, a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member. The outer diameter of the portion where the second inner ring is fitted to the shaft member before the first inner ring is fitted onto the shaft member is the portion of the outer peripheral surface of the shaft member where the second inner ring is fitted. , Larger than the outer diameter in the state before the second inner ring is press fitted into the shaft member,
    The double row tapered roller bearing unit according to claim 1.
  3. 　前記段部の周囲で、第１内輪の小径側端面と第２内輪の小径側端面との間に間座が挟持されている、請求項２に記載の複列円すいころ軸受ユニット。 The double-row tapered roller bearing unit according to claim 2, wherein a spacer is sandwiched between the small-diameter side end surface of the first inner ring and the small-diameter side end surface of the second inner ring around the stepped portion.
  4. 　第１内輪および第２内輪の諸元が実質的に等しい、請求項２に記載の複列円すいころ軸受ユニット。 The double-row tapered roller bearing unit according to claim 2, wherein the specifications of the first inner ring and the second inner ring are substantially equal.
  5. 　前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分とが互いに連続した単一円筒面により構成されており、前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法が、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法よりも小さい、請求項１に記載の複列円すいころ軸受ユニット。 Of the outer peripheral surface of the shaft member, a portion on which the first inner ring is fitted and a portion on which the second inner ring is fitted are configured by a single cylindrical surface that is continuous with each other. The inner diameter dimension of the first inner ring in a state before the outer fitting is press-fitted by press-fitting is smaller than the inner diameter dimension of the second inner ring in a state before the second inner ring is fitted on the shaft member by press-fitting. Double row tapered roller bearing unit as described in 1.
  6. 　第１内輪が、内周面と大径側端面との連続部にＲ面取り部を有し、
    　第２内輪が、内周面と大径側端面との連続部に、曲率半径が第１内輪のＲ面取り部の曲率半径よりも大きいＲ面取り部、または、軸方向幅寸法および径方向幅寸法が第１内輪のＲ面取り部の曲率半径よりも大きいＣ面取り部を有し、
    　前記軸部材は、外周面のうち、第２内輪が外嵌される部分の軸方向他側に隣接する部分に、車輪を支持固定するための回転側フランジを有し、かつ、第２内輪のＲ面取り部またはＣ面取り部と対向する位置に存在する、前記軸部材の外周面と前記回転側フランジの軸方向片側面との連続部に、これらの面同士を滑らかに連続させる断面円弧形の隅Ｒ部を有する、
    　請求項５に記載の複列円すいころ軸受ユニット。     The first inner ring has an R chamfered portion at a continuous portion between the inner peripheral surface and the large-diameter end surface,
    The second inner ring has an R chamfered portion where the radius of curvature is larger than the radius of curvature of the R chamfered portion of the first inner ring, or an axial width dimension and a radial width dimension at a continuous portion between the inner peripheral surface and the large-diameter side end surface. Has a C chamfer that is larger than the radius of curvature of the R chamfer of the first inner ring,
    The shaft member has a rotation side flange for supporting and fixing the wheel at a portion adjacent to the other side in the axial direction of the portion where the second inner ring is fitted on the outer peripheral surface, and the second inner ring A cross-sectional arc shape that smoothly exists between the outer peripheral surface of the shaft member and the axial one side surface of the rotation side flange, which exists at a position facing the R chamfered portion or the C chamfered portion. Having a corner R portion,
    The double row tapered roller bearing unit according to claim 5.
  7. 　内周面に、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面によりそれぞれ構成された、第１外輪軌道および第２外輪軌道を有する外径側軌道輪部材と、
    　外周面に、軸方向に関して互いに離れる方向に向かうほど直径が大きくなる方向に傾斜した部分円すい面によりそれぞれ構成された、第１内輪軌道および第２外輪軌道を有する内径側軌道輪部材と、
    　第１外輪軌道と第１内輪軌道との間、および、第２外輪軌道と第２内輪軌道との間に、それぞれ複数個ずつ転動自在に設けられた円すいころと、
    を備え、
    　前記内径側軌道輪部材は、外周面に第１内輪軌道が形成された第１内輪と、外周面に第２内輪軌道が形成された第２内輪と、軸部材とを備え、第１内輪および第２内輪が、前記軸部材に圧入により外嵌され、かつ、該軸部材の軸方向片端部に塑性変形により形成されたかしめ部により、第１内輪の大径側端面を抑え付けることで、第１内輪および第２内輪が前記軸部材に結合固定されることにより構成された、
    複列円すいころ軸受ユニットの製造方法であって、
    　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪軌道の傾斜角度θ1と、
    　前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪軌道の傾斜角度θ2と、
    　前記軸部材に第１内輪を圧入により外嵌することに伴って生じる第１内輪軌道の傾斜角度減少量δθaと、
    　前記軸部材に第２内輪を圧入により外嵌することに伴って生じる第２内輪軌道の傾斜角度減少量δθbと、
    　前記かしめ部を形成することに伴って生じる第１内輪軌道の傾斜角度増大量δθkとを調整することにより、
    　前記かしめ部を形成した後の状態での第１内輪軌道の傾斜角度φ1と第２内輪軌道の傾斜角度Θ2とを、それぞれの適正範囲内に収めることを特徴とする、
    複列円すいころ軸受ユニットの製造方法。     An outer-diameter-side track ring member having a first outer ring raceway and a second outer ring raceway, each of which is constituted by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the inner peripheral surface;
    An inner diameter side race ring member having a first inner ring raceway and a second outer ring raceway, each formed by a partial conical surface inclined in a direction in which the diameter increases in a direction away from each other with respect to the axial direction on the outer peripheral surface;
    A plurality of tapered rollers each provided between the first outer ring raceway and the first inner ring raceway and between the second outer ring raceway and the second inner ring raceway;
    With
    The inner diameter side race ring member includes a first inner ring having a first inner ring raceway formed on an outer peripheral surface, a second inner ring having a second inner ring raceway formed on an outer peripheral surface, and a shaft member. The second inner ring is externally fitted to the shaft member by press fitting, and the large-diameter side end surface of the first inner ring is suppressed by a caulking portion formed by plastic deformation at one axial end portion of the shaft member. The first inner ring and the second inner ring are configured by being coupled and fixed to the shaft member.
    A method of manufacturing a double row tapered roller bearing unit,
    An inclination angle θ 1 of the first inner ring raceway in a state before the first inner ring is fitted onto the shaft member by press fitting;
    An inclination angle θ 2 of the second inner ring raceway in a state before the second inner ring is fitted over the shaft member by press fitting;
    A tilt angle reduction amount δθ a of the first inner ring raceway that is generated when the first inner ring is fitted onto the shaft member by press fitting;
    A tilt angle reduction amount δθ b of the second inner ring raceway that is generated when the second inner ring is fitted on the shaft member by press fitting;
    By adjusting the amount of increase δθ k of the inclination angle of the first inner ring race that is caused by forming the caulking portion,
    The inclination angle φ 1 of the first inner ring raceway and the inclination angle Θ 2 of the second inner ring raceway in a state after the caulking portion is formed are within appropriate ranges,
    Manufacturing method of double row tapered roller bearing unit.
  8. 　前記傾斜角度θ1と前記傾斜角度θ2とを実質的に等しくし、次式：
    　δθa（ΔＸ1）－δθb（ΔＸ2）＝δθk　
    を満たすように、前記調整を行う、
    請求項７に記載の複列円すいころ軸受ユニットの製造方法。     The inclination angle θ 1 and the inclination angle θ 2 are made substantially equal, and the following formula:
    δθ a (ΔX 1 ) −δθ b (ΔX 2 ) = δθ k
    Make the adjustments to satisfy
    The manufacturing method of the double row tapered roller bearing unit of Claim 7.
  9. 　前記軸部材に対する前記第１内輪の圧入代ΔＸ1を調整することにより、前記傾斜角度減少量δθaを調整し、
    　前記軸部材に対する前記第２内輪の圧入代ΔＸ2を調整することにより、前記傾斜角度減少量δθbを調整する、
    　請求項７に記載の複列円すいころ軸受ユニットの製造方法。     By adjusting the press-fit allowance ΔX 1 of the first inner ring with respect to the shaft member, the inclination angle reduction amount δθ a is adjusted,
    Adjusting the tilt angle reduction amount δθ b by adjusting the press-fit allowance ΔX 2 of the second inner ring with respect to the shaft member;
    The manufacturing method of the double row tapered roller bearing unit of Claim 7.
  10. 　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法と、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法とを実質的に等しくし、
    　前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分との間に段部を設け、前記軸部材の外周面のうちの第１内輪が外嵌される部分の、該軸部材に第１内輪を圧入により外嵌する前の状態での外径寸法を、前記軸部材の外周面のうちの第２内輪が外嵌される部分の、該軸部材に第２内輪を圧入により外嵌する前の状態での外径寸法よりも大きくして、前記圧入代ΔＸ１、ΔＸ２をそれぞれ調整する、請求項９に記載の複列円すいころ軸受ユニットの製造方法。     The inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting. And substantially equal,
    Of the outer peripheral surface of the shaft member, a step is provided between a portion where the first inner ring is fitted and a portion where the second inner ring is fitted, and the first inner ring of the outer peripheral surface of the shaft member is The outer diameter of the part to be externally fitted before the first inner ring is externally fitted to the shaft member by press-fitting, the part of the outer peripheral surface of the shaft member to which the second inner ring is externally fitted, 10. The double-row tapered roller according to claim 9, wherein the press-fitting allowances ΔX 1 and ΔX 2 are respectively adjusted to be larger than an outer diameter dimension in a state before the second inner ring is externally fitted to the shaft member by press-fitting. Manufacturing method of bearing unit.
  11. 　前記段部の周囲で、第１内輪の小径側端面と第２内輪の小径側端面との間に間座を挟持する、請求項１０に記載の複列円すいころ軸受ユニットの製造方法。 The method for manufacturing a double row tapered roller bearing unit according to claim 10, wherein a spacer is sandwiched between the small diameter side end surface of the first inner ring and the small diameter side end surface of the second inner ring around the stepped portion.
  12. 　第１内輪および第２内輪の諸元を実質的に等しくする、請求項７に記載の複列円すいころ軸受ユニットの製造方法。 The method for manufacturing a double-row tapered roller bearing unit according to claim 7, wherein the specifications of the first inner ring and the second inner ring are substantially equal.
  13. 　前記軸部材の外周面のうち、第１内輪が外嵌される部分と第２内輪が外嵌される部分とを互いに連続した単一円筒面とし、
    　前記軸部材に第１内輪を圧入により外嵌する前の状態での第１内輪の内径寸法を、前記軸部材に第２内輪を圧入により外嵌する前の状態での第２内輪の内径寸法よりも小さくして、前記圧入代ΔＸ１、ΔＸ２をそれぞれ調整する、請求項９に記載の複列円すいころ軸受ユニットの製造方法。     Of the outer peripheral surface of the shaft member, a portion where the first inner ring is fitted and a portion where the second inner ring is fitted are a single cylindrical surface which is continuous with each other,
    The inner diameter of the first inner ring before the first inner ring is fitted onto the shaft member by press fitting, and the inner diameter of the second inner ring before the second inner ring is fitted onto the shaft member by press fitting. The manufacturing method of the double row tapered roller bearing unit according to claim 9, wherein the press-fitting allowances ΔX 1 and ΔX 2 are respectively adjusted to be smaller.
  14. 　第１内輪の内周面と大径側端面との連続部に、Ｒ面取り部を設け、
    　第２内輪の内周面と大径側端面との連続部に、第１内輪のＲ面取り部の曲率半径よりも大きな曲率半径を有するＲ面取り部、または、第１内輪のＲ面取り部の曲率半径よりも大きい、軸方向幅寸法および径方向幅寸法を有するＣ面取り部を設け、
    　前記軸部材の外周面のうち、第２内輪を外嵌する部分の軸方向他側に隣接する部分に、車輪を支持固定するための回転側フランジを設け、かつ、第２内輪のＲ面取り部またはＣ面取り部と対向する位置に存在する、前記軸部材の外周面と前記回転側フランジの軸方向片側面との連続部に、これらの面同士を滑らかに連続させる断面円弧形の隅Ｒ部を設ける、
    　請求項１３に記載の複列円すいころ軸受ユニットの製造方法。     An R chamfered portion is provided at a continuous portion between the inner peripheral surface of the first inner ring and the large-diameter side end surface,
    The curvature of the R chamfered portion having a radius of curvature larger than the radius of curvature of the R chamfered portion of the first inner ring or the curvature of the R chamfered portion of the first inner ring at the continuous portion between the inner peripheral surface of the second inner ring and the large-diameter end surface. Providing a C chamfer having an axial width dimension and a radial width dimension larger than the radius;
    Of the outer peripheral surface of the shaft member, a rotation side flange for supporting and fixing the wheel is provided in a portion adjacent to the other side in the axial direction of the portion fitting the second inner ring, and the R chamfered portion of the second inner ring Or the corner | angular area R of the circular arc section which exists in the position which opposes a C chamfering part, and makes these surfaces smoothly continue in the continuous part of the outer peripheral surface of the said shaft member and the axial direction one side surface of the said rotation side flange. Provide a part,
    The manufacturing method of the double row tapered roller bearing unit of Claim 13.
PCT/JP2014/076215 2013-10-04 2014-09-30 Double-row tapered roller bearing unit and method for manufacturing same WO2015050143A1 (en)

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CN105518321A (en) 2016-04-20
US9581192B2 (en) 2017-02-28
US20160245334A1 (en) 2016-08-25
EP3054184A1 (en) 2016-08-10
EP3054184B1 (en) 2018-11-07

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